U.S. patent application number 15/765101 was filed with the patent office on 2018-10-04 for cold storage heat exchanger.
The applicant listed for this patent is DENSO CORPORATION. Invention is credited to Jun ABEI, Naohisa ISHIZAKA, Norihide KAWACHI, Yuusuke KITOU, Toshiya NAGASAWA, Masakazu NAGAYA, Ken NISHIMURA, Eiichi TORIGOE.
Application Number | 20180281553 15/765101 |
Document ID | / |
Family ID | 58492196 |
Filed Date | 2018-10-04 |
United States Patent
Application |
20180281553 |
Kind Code |
A1 |
ABEI; Jun ; et al. |
October 4, 2018 |
COLD STORAGE HEAT EXCHANGER
Abstract
A cold storage heat exchanger includes: a plurality of
refrigerant tubes disposed at intervals, each of the refrigerant
tubes including a refrigerant passage that allows a refrigerant to
flow therethrough; a cold storage material adjacent to the
refrigerant tubes; and a heat transfer suppressor that suppresses
heat transfer from the refrigerant tubes to the cold storage
material in an overheated area of the refrigerant formed in the
refrigerant passage.
Inventors: |
ABEI; Jun; (Kariya-city,
JP) ; NAGASAWA; Toshiya; (Kariya-city, JP) ;
TORIGOE; Eiichi; (Kariya-city, JP) ; ISHIZAKA;
Naohisa; (Kariya-city, JP) ; KAWACHI; Norihide;
(Kariya-city, JP) ; KITOU; Yuusuke; (Kariya-city,
JP) ; NISHIMURA; Ken; (Kariya-city, JP) ;
NAGAYA; Masakazu; (Kariya-city, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
DENSO CORPORATION |
Kariya-city, Aichi-pref. |
|
JP |
|
|
Family ID: |
58492196 |
Appl. No.: |
15/765101 |
Filed: |
September 23, 2016 |
PCT Filed: |
September 23, 2016 |
PCT NO: |
PCT/JP2016/077976 |
371 Date: |
March 30, 2018 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
B60H 1/3227 20130101;
B60H 1/005 20130101; Y02E 60/14 20130101; B60H 1/00335
20130101 |
International
Class: |
B60H 1/00 20060101
B60H001/00; B60H 1/32 20060101 B60H001/32 |
Foreign Application Data
Date |
Code |
Application Number |
Oct 1, 2015 |
JP |
2015-195818 |
Sep 6, 2016 |
JP |
2016-173410 |
Claims
1. A cold storage heat exchanger (40, 401, 140, 1401, 240, 2401,
340, 440, 540, 1040, 1140, 1240, 1340, 1440, 1540, 1640, 1740,
1840) comprising: a plurality of refrigerant tubes (45) disposed at
intervals, each of the refrigerant tubes including a refrigerant
passage that allows a refrigerant to flow therethrough; a cold
storage material (50) adjacent to the refrigerant tubes; and a heat
transfer suppressor (47b, 471b, 147, 1471, 247, 2471, 347b, 447,
547, 1045, 1147b, 1247, 1347) that suppresses heat transfer from
the refrigerant tubes to the cold storage material in an overheated
area (S, S1, S2) of the refrigerant formed in the refrigerant
passage.
2. The cold storage heat exchanger according to claim 1, further
comprising: a plurality of cold storage material containers (47,
471, 147, 1471, 247, 2471, 347, 447, 547, 1147, 1247, 1347) that
are adjacent to the refrigerant tubes and store the cold storage
material.
3. The cold storage heat exchanger according to claim 2, wherein:
each of the cold storage material containers is disposed between
two of the refrigerant tubes with a longitudinal direction of the
cold storage material container aligned with an extending direction
of the refrigerant tubes and joined to the two refrigerant tubes;
and an air passage (53) formed in a space between another one of
the refrigerant tubes and each of the two refrigerant tubes joined
to each of the cold storage material containers at a side opposite
to the cold storage material container for heat exchange between
air flowing through the space and the refrigerant.
4. The cold storage heat exchanger (40, 401, 140, 1401, 240, 2401,
340, 440, 540, 1640, 1840) according to claim 3, wherein the heat
transfer suppressor (47b, 471b, 147, 1471, 247, 2471, 347b, 447,
547) suppresses heat transfer from the refrigerant tubes to the
cold storage material in the overheated area (S) formed by
evaporation of the refrigerant near an outlet of the refrigerant
passage.
5. The cold storage heat exchanger (40, 401, 340) according to
claim 4, further comprising an inner fin (47b, 471b, 347b) that
extends in a longitudinal direction that is the extending direction
of the refrigerant tubes inside the cold storage material
container, wherein: the inner fin is configured in such a manner
that, in the cold storage material container joined to the
refrigerant tube having the overheated area, a heat transfer amount
from the refrigerant tube to the cold storage material through the
inner fin is relatively small in a part that is in contact with the
overheated area of the refrigerant tube and a heat transfer amount
from the refrigerant tube to the cold storage material through the
inner fin is relatively large in a part that is in contact with an
area other than the overheated area of the refrigerant tube; and
the heat transfer suppressor includes the inner fin.
6. The cold storage heat exchanger (401) according to claim 5,
wherein in the cold storage material container joined to the
refrigerant tube having the overheated area, the inner fin (471b)
has a relatively low joining ratio with an inner wall of the cold
storage material container in a part that is in contact with the
overheated area of the refrigerant tube and the inner fin (471b)
has a relatively high joining ratio with the inner wall of the cold
storage material container in a part that is in contact with an
area other than the overheated area of the refrigerant tube.
7. The cold storage heat exchanger (40, 340) according to claim 5,
wherein in the cold storage material container joined to the
refrigerant tube having the overheated area, the inner fin (47b,
347b) is not joined to an inner wall of the cold storage material
container in a part that is in contact with the overheated area of
the refrigerant tube and the inner fin (47b, 347b) is joined to the
inner wall of the cold storage material container in a part that is
in contact with an area other than the overheated area of the
refrigerant tube.
8. The cold storage heat exchanger (40) according to claim 7,
wherein: the plurality of refrigerant tubes include at least two
refrigerant tubes disposed in an airflow direction of the air in
the air passage; the cold storage material container is joined to
the at least two refrigerant tubes disposed in the airflow
direction; the inner fin (47b) overlaps the at least two
refrigerant tubes when viewed in an array direction of the
refrigerant tubes and the cold storage material container; and in
the cold storage material container joined to the at least two
refrigerant tubes including a refrigerant tube having the
overheated area, the inner fin is not joined to the inner wall of
the cold storage material container in an area that includes a part
that is in contact with the overheated area of the refrigerant tube
and overlaps the part in contact with the overheated area of the
refrigerant tube when viewed in the airflow direction and the inner
fin is joined to the inner wall of the cold storage material
container in the other area.
9. The cold storage heat exchanger (340) according to claim 7,
wherein: the plurality of refrigerant tubes include at least two
refrigerant tubes disposed in an airflow direction of the air in
the air passage; the cold storage material container is joined to
the at least two refrigerant tubes disposed in the airflow
direction; the inner fin (347b) overlaps the at least two
refrigerant tubes when viewed in an array direction of the
refrigerant tubes and the cold storage material container; and in
the cold storage material container joined to the at least two
refrigerant tubes including a refrigerant tube having the
overheated area, the inner fin is joined to the inner wall of the
cold storage material container over the entire area in the
longitudinal direction that is the extending direction of the
refrigerant tubes in an area overlapping a refrigerant tube having
no overheated area, and the inner fin is not joined to the inner
wall of the cold storage material container in a part that is in
contact with the overheated area of the refrigerant tube and joined
to the inner wall of the cold storage material container in the
other part in an area overlapping the refrigerant tube having the
overheated area.
10. The cold storage heat exchanger (140, 1401, 440) according to
any one of claims 4 to 9, wherein: the cold storage material
container (147, 1471, 447) joined to the refrigerant tube having
the overheated area is configured in such a manner that a heat
transfer amount from the refrigerant tube to the cold storage
material through the cold storage material container is relatively
small in a part that is in contact with the overheated area of the
refrigerant tube and a heat transfer amount from the refrigerant
tube to the cold storage material through the cold storage material
container is relatively large in a part that is in contact with an
area other than the overheated area of the refrigerant tube; and
the heat transfer suppressor includes the cold storage material
container.
11. The cold storage heat exchanger (1401) according to claim 10,
wherein the cold storage material container (1471) joined to the
refrigerant tube having the overheated area has a relatively low
joining ratio with the refrigerant tube in a part that is in
contact with the overheated area of the refrigerant tube and has a
relatively high joining ratio with the refrigerant tube in a part
that is in contact with an area other than the overheated area of
the refrigerant tube.
12. The cold storage heat exchanger (140, 440) according to claim
10, wherein the cold storage material container (147, 447) joined
to the refrigerant tube having the overheated area is separated
from the refrigerant tube without being joined to the refrigerant
tube in a part that is in contact with the overheated area of the
refrigerant tube and joined to the refrigerant tube in a part that
is in contact with an area other than the overheated area of the
refrigerant tube.
13. The cold storage heat exchanger (140) according to claim 12,
wherein: the plurality of refrigerant tubes include at least two
refrigerant tubes disposed in an airflow direction of the air in
the air passage; the cold storage material container is joined to
the at least two refrigerant tubes disposed in the airflow
direction; and the cold storage material container (147) joined to
the at least two refrigerant tubes including a refrigerant tube
having the overheated area is separated from the refrigerant tubes
without being joined to the refrigerant tubes in an area that
includes a part that is in contact with the overheated area of the
refrigerant tube and overlaps the part in contact with the
overheated area of the refrigerant tube when viewed in the airflow
direction and joined to the refrigerant tubes in the other
area.
14. The cold storage heat exchanger (440) according to claim 12,
wherein: the plurality of refrigerant tubes include at least two
refrigerant tubes disposed in an airflow direction of the air in
the air passage; the cold storage material container is joined to
the at least two refrigerant tubes disposed in the air flow
direction; and the cold storage material container (447) joined to
the at least two refrigerant tubes including a refrigerant tube
having the overheated area is joined to the refrigerant tubes over
the entire area in the extending direction in an area overlapping a
refrigerant tube having no overheated area, and is separated from
the refrigerant tubes without being joined to the refrigerant tubes
in a part that is in contact with the overheated area of the
refrigerant tube and joined to the refrigerant tubes in the other
part in an area overlapping the refrigerant tube having the
overheated area.
15. The cold storage heat exchanger (240, 2401, 540) according to
claim 4, further comprising: an inner fin that extends in the
longitudinal direction that is the extending direction of the
refrigerant tubes inside the cold storage material container, and
is joined to an inner wall of the cold storage material container,
wherein: the cold storage material container (247, 2471, 547)
joined to the refrigerant tube having the overheated area is
configured in such a manner that a heat transfer amount from the
refrigerant tube to the cold storage material through the cold
storage material container is relatively small in a part that is in
contact with the overheated area of the refrigerant tube and a heat
transfer amount from the refrigerant tube to the cold storage
material through the cold storage material container is relatively
large in a part that is in contact with an area other than the
overheated area of the refrigerant tube; and the heat transfer
suppressor includes the cold storage material container.
16. The cold storage heat exchanger (2401) according to claim 15,
wherein the cold storage material container (2471) joined to the
refrigerant tube having the overheated area has a relatively low
joining ratio with the refrigerant tube in a part that is in
contact with the overheated area of the refrigerant tube and has a
relatively high joining ratio with the refrigerant tube in a part
that is in contact with an area other than the overheated area of
the refrigerant tube.
17. The cold storage heat exchanger (240, 540) according to claim
15, wherein the cold storage material container (247, 547) joined
to the refrigerant tube having the overheated area is separated
from the refrigerant tube without being joined to the refrigerant
tube in a part that is in contact with the overheated area of the
refrigerant tube and is joined to the refrigerant tube in a part
that is in contact with an area other than the overheated area of
the refrigerant tube.
18. The cold storage heat exchanger (240) according to claim 17,
wherein: the plurality of refrigerant tubes include at least two
refrigerant tubes disposed in an airflow direction of the air in
the air passage; the cold storage material container is joined to
the at least two refrigerant tubes disposed in the airflow
direction; the inner fin overlaps the at least two refrigerant
tubes when viewed in an array direction of the refrigerant tubes
and the cold storage material container; and the cold storage
material container (247) joined to the at least two refrigerant
tubes including a refrigerant tube having the overheated area is
separated from the refrigerant tubes without being joined to the
refrigerant tubes in an area that includes a part that is in
contact with the overheated area of the refrigerant tube and
overlaps the part in contact with the overheated area of the
refrigerant tube when viewed in the airflow direction and is joined
to the refrigerant tubes in the other area.
19. The cold storage heat exchanger (540) according to claim 17,
wherein: the plurality of refrigerant tubes include at least two
refrigerant tubes disposed in an airflow direction of the air in
the air passage; the cold storage material container is joined to
the at least two refrigerant tubes disposed in the airflow
direction; the inner fin overlaps the at least two refrigerant
tubes when viewed in an array direction of the refrigerant tubes
and the cold storage material container; and the cold storage
material container (547) joined to the at least two refrigerant
tubes including a refrigerant tube having the overheated area is
joined to the refrigerant tubes over the entire area in the
extending direction in an area overlapping a refrigerant tube
having no overheated area, and is separated from the refrigerant
tubes without being joined to the refrigerant tubes in a part that
is in contact with the overheated area of the refrigerant tube and
joined to the refrigerant tubes in the other part, in an area
overlapping the refrigerant tube having the overheated area.
20. The cold storage heat exchanger (1840) according to any one of
claims 4 to 19, wherein the cold storage material container joined
to the refrigerant tube having the overheated area (S) is not
disposed in a part that is in contact with the overheated area of
the refrigerant tube and disposed only in a part that is in contact
with an area other than the overheated area of the refrigerant
tube.
21. The cold storage heat exchanger (1640) according to any one of
claims 1 to 19, wherein a part of the cold storage material that is
in contact with at least the overheated area (S) is a high-melting
point cold storage material (50A) having a relatively high melting
point compared to the other part.
22. The cold storage heat exchanger (1040, 1140, 1240, 1340, 1440,
1540) according to claim 2 or 3, further comprising: a first header
tank (51) communicating with one end side of each of the plurality
of refrigerant tubes, a longitudinal direction of the first header
tank being aligned with an array direction of the refrigerant tubes
and the cold storage material containers; and a second header tank
(52) communicating with the other end side of each of the plurality
of refrigerant tubes, a longitudinal direction of the second header
tank being aligned with the array direction, wherein: the plurality
of refrigerant tubes are arranged in two rows so as to be paired in
an airflow direction of the air in the air passage; an inside of
the first header tank is partitioned into an inlet side passage
(1041) that communicates with some of the plurality of refrigerant
tubes disposed on a downstream side in the airflow direction and
includes an inlet of the refrigerant passage on one end in the
longitudinal direction that is an extending direction of the
refrigerant tubes and an outlet side passage (1043) that
communicates with some of the plurality of refrigerant tubes
disposed on an upstream side in the airflow direction and includes
an outlet of the refrigerant passage on one end or the other end in
the longitudinal direction that is the extending direction of the
refrigerant tubes; the plurality of refrigerant tubes are divided
into a first group (G1) that communicates with the inlet side
passage and is disposed on the one end side in the longitudinal
direction that is the extending direction of the refrigerant tubes,
a second group (G2) that communicates with the inlet side passage
and is disposed on the other end side in the longitudinal direction
that is the extending direction of the refrigerant tubes, a third
group (G3) that communicates with the outlet side passage and is
disposed on the other end side in the longitudinal direction that
is the extending direction of the refrigerant tubes, and a fourth
group (G4) that communicates with the outlet side passage and is
disposed on the one end side in the longitudinal direction that is
the extending direction of the refrigerant tubes; the second header
tank allows communication between the first group and the third
group and communication between the second group and the fourth
group, and changes a position of the refrigerant introduced to the
one end side in the longitudinal direction that is the extending
direction of the refrigerant tubes from the inlet side passage and
a position of the refrigerant introduced to the other end side in
the longitudinal direction from the inlet side passage to the other
end side and the one end side, respectively, so as to be led to the
outlet side passage; the overheated area (S1) is formed in the
second group and the fourth group of the plurality of the
refrigerant tubes; and the heat transfer suppressor (1045, 1147b,
1247, 1347) includes a refrigerant passage structure (1045) having
a structure in which the cold storage material container is joined
to both of the second group having the overheated area and the
third group having no overheated area and a structure in which the
cold storage material container is joined to both of the first
group having no overheated area and the fourth group having the
overheated area.
23. The cold storage heat exchanger (1140) according to claim 22,
further comprising an inner fin (1147b) that extends in the
longitudinal direction that is the extending direction of the
refrigerant tubes inside the cold storage material container,
wherein: the inner fin is configured in such a manner that a heat
transfer amount from the refrigerant tube to the cold storage
material through the inner fin is relatively small in a part where
the cold storage material container is joined to the second group
and the fourth group of the refrigerant tubes having the overheated
area and a heat transfer amount from the refrigerant tube to the
cold storage material through the inner fin is relatively large in
a part where the cold storage material container is joined to the
first group and the third group of the refrigerant tubes having no
overheated area; and the heat transfer suppressor includes the
inner fin.
24. The cold storage heat exchanger according to claim 23, wherein
the inner fin has a relatively low joining ratio with an inner wall
of the cold storage material container in a part where the cold
storage material container is joined to the second group and the
fourth group of the refrigerant tubes having the overheated area
and a relatively high joining ratio with the inner wall of the cold
storage material container in a part where the cold storage
material container is in contact with the first group and the third
group of the refrigerant tubes having no overheated area.
25. The cold storage heat exchanger according to claim 23, wherein
the inner fin is not joined to an inner wall of the cold storage
material container in a part where the cold storage material
container is joined to the second group and the fourth group of the
refrigerant tubes having the overheated area and the inner fin is
joined to the inner wall of the cold storage material container in
a part where the cold storage material container is in contact with
the first group and the third group of the refrigerant tubes having
no overheated area.
26. The cold storage heat exchanger (1240) according to any one of
claims 22 to 25, wherein: the cold storage material container
(1247) is configured in such a manner that a heat transfer amount
from the refrigerant tube to the cold storage material through the
cold storage material container is relatively small in a part that
is in contact with the second group and the fourth group of the
refrigerant tubes having the overheated area and a heat transfer
amount from the refrigerant tube to the cold storage material
through the cold storage material container is relatively large in
a part that is in contact with the first group and the third group
of the refrigerant tubes having no overheated area; and the heat
transfer suppressor includes the cold storage material
container.
27. The cold storage heat exchanger according to claim 26, wherein
the cold storage material container has a relatively low joining
ratio with the refrigerant tube in a part that is in contact with
the second group and the fourth group of the refrigerant tubes
having the overheated area and a relatively high joining ratio with
the refrigerant tube in a part that is in contact with the first
group and the third group of the refrigerant tubes having no
overheated area.
28. The cold storage heat exchanger according to claim 26, wherein
the cold storage material container is separated from the
refrigerant tube without being joined to the refrigerant tube in a
part that is in contact with the second group and the fourth group
of the refrigerant tubes having the overheated area and the cold
storage material container is joined to the refrigerant tube in a
part that is in contact with the first group and the third group of
the refrigerant tubes having no overheated area.
29. The cold storage heat exchanger (1340) according to claim 22,
further comprising an inner fin that extends in the longitudinal
direction that is an extending direction of the refrigerant tubes
inside the cold storage material container, and is joined to an
inner wall of the cold storage material container, wherein: the
cold storage material container (1347) is configured in such a
manner that a heat transfer amount from the refrigerant tube to the
cold storage material through the cold storage material container
is relatively small in a part that is in contact with the second
group and the fourth group of the refrigerant tubes having the
overheated area and a heat transfer amount from the refrigerant
tube to the cold storage material through the cold storage material
container is relatively large in a part that is in contact with the
first group and the third group of the refrigerant tubes having no
overheated area; and the heat transfer suppressor includes the cold
storage material container.
30. The cold storage heat exchanger according to claim 29, wherein
the cold storage material container has a relatively low joining
ratio with the refrigerant tube in a part that is in contact with
the second group and the fourth group of the refrigerant tubes
having the overheated area and has a relatively high joining ratio
with the refrigerant tube in a part that is in contact with the
first group and the third group of the refrigerant tubes having no
overheated area.
31. The cold storage heat exchanger according to claim 29, wherein
the cold storage material container is separated from the
refrigerant tube without being joined to the refrigerant tube in a
part that is in contact with the second group and the fourth group
of the refrigerant tubes having the overheated area and joined to
the refrigerant tube in a part that is in contact with the first
group and the third group of the refrigerant tubes having no
overheated area.
32. The cold storage heat exchanger (1040B) according to any one of
claims 22 to 31, wherein a plurality of the refrigerant passage
structures each included as the heat transfer suppressor are
disposed in the longitudinal direction that is an extending
direction of the refrigerant tubes.
33. The cold storage heat exchanger (1440, 1540) according to any
one of claims 22 to 32, wherein a part of the cold storage material
that is in contact with at least the overheated area (S1) is a
high-melting point cold storage material (50A) having a relatively
high melting point compared to the other part.
34. The cold storage heat exchanger (1440) according to claim 33,
wherein: the overheated area includes a second overheated area (S2)
that is formed near the outlet side passage in the third group of
the plurality of the refrigerant tubes; and the high-melting point
cold storage material is disposed in a part that is in contact with
the second group and the fourth group having the overheated area
(S1), and the high-melting point cold storage material is disposed
in a part that is in contact with the third group having the second
overheated area (S2) in the plurality of refrigerant tubes.
35. The cold storage heat exchanger (1440) according to claim 33,
wherein: the overheated area includes a second overheated area (S2)
that is formed near the outlet side passage in the third group of
the plurality of the refrigerant tubes; the high-melting point cold
storage material is disposed in a part that is in contact with the
second group and the fourth group having the overheated area (S1)
in the plurality of refrigerant tubes; and the high-melting point
cold storage material is disposed in a part that is in contact with
the vicinity of the outlet side passage having the second
overheated area (S2) in the third group of the plurality of
refrigerant tubes.
36. The cold storage heat exchanger (1540) according to claim 33,
wherein the high-melting point cold storage material is disposed in
a part that is in contact with the second group and the fourth
group having the overheated area (S1) in the plurality of
refrigerant tubes.
37. The cold storage heat exchanger (1740) according to any one of
claims 2 to 36, further comprising: at least a pair of partition
plates (47d) that is disposed inside the cold storage material
container and partitions an internal space of the cold storage
material container in the longitudinal direction that is an
extending direction of the refrigerant tubes, wherein one of the
partition plates has a space in an end on one side in the
longitudinal direction of the cold storage material container, and
the other one of the partition plates has a space in an end on the
other side in the longitudinal direction of the cold storage
material container.
Description
CROSS REFERENCE TO RELATED APPLICATION
[0001] This application is based on Japanese Patent Application No.
2015-195818 filed on Oct. 1, 2015 and Japanese Patent Application
No. 2016-173410 filed on Sep. 6, 2016, and claims the benefit of
the priority, the disclosure of which is incorporated herein by
reference in its entirety.
TECHNICAL FIELD
[0002] The present disclosure relates to a cold storage heat
exchanger to evaporate refrigerant, which configures a
refrigerating cycle together with a compressor compressing and
discharging refrigerant, a radiator cooling high-temperature
refrigerant, and a decompressor decompressing the cooled
refrigerant.
BACKGROUND ART
[0003] A refrigerating cycle apparatus has been conventionally used
in an air conditioner. Many attempts have been made to provide a
limited cooling operation even when the refrigerating cycle
apparatus is in a stopped state. For example, in a vehicle air
conditioner, a refrigerating cycle apparatus is driven by an engine
for traveling. Thus, when the engine comes to a stop during a
temporal stop of the vehicle, the refrigerating cycle apparatus
also comes to a stop. There has been proposed a cold storage heat
exchanger that includes a cold storage material added to an
evaporator of a refrigerating cycle apparatus in order to provide a
limited cooling operation during such a temporal stop of the
vehicle. For example, a cold storage heat exchanger described in
Patent Literature 1 is known.
PRIOR ART LITERATURES
Patent Literature
[0004] Patent Literature 1: JP 2010-91250 A
SUMMARY OF INVENTION
[0005] Typically, in a refrigerating cycle apparatus, a compressor
for compressing and ejecting a refrigerant is present on the
downstream side in the flow of the refrigerant relative to a cold
storage heat exchanger. A return of the refrigerant in a liquid
state to the compressor causes a failure. Thus, it is typically
necessary to completely evaporate the refrigerant at an outlet of
the cold storage heat exchanger. In the cold storage heat
exchanger, the refrigerant forms a single gas layer near an outlet
of a refrigerant passage, and the pressure thereof exceeds the
saturated vapor pressure. As a result, there is a part where a
refrigerant temperature rapidly transitions to a high temperature,
that is, an overheated area. Further, when a flow rate of the
refrigerant is low, there may be an imbalance in the flow of the
refrigerant depending on the arrangement of the refrigerant passage
inside the cold storage heat exchanger, which may form an
overheated area in a part where the refrigerant is difficult to
flow. In this manner, an overheated area may be present at any
location on the refrigerant passage in the cold storage heat
exchanger.
[0006] In the conventional cold storage heat exchanger described in
Patent Literature 1, a cold storage material is typically disposed
adjacent to a refrigerant tube that constitutes a refrigerant
passage and cooled by a refrigerant flowing through the refrigerant
tube. The inventor has made a close study and found out the
following issue. When an overheated area is formed on a refrigerant
tube, the temperature of a refrigerant in the overheated area
becomes high. Thus, a cold storage material is less cooled due to
the influence of the overheated area. As a result, a cold storage
performance of the cold storage heat exchanger may be
deteriorated.
[0007] It is an object of the present disclosure to provide a cold
storage heat exchanger which can secure a cold storage performance,
while there is an overheated area, by reducing influence of the
overheated area.
[0008] According to an aspect of the present disclosure, a cold
storage heat exchanger includes: a plurality of refrigerant tubes
disposed at intervals, each of the refrigerant tubes including a
refrigerant passage that allows a refrigerant to flow therethrough;
a cold storage material adjacent to the refrigerant tubes; and a
heat transfer suppressor that suppresses heat transfer from the
refrigerant tubes to the cold storage material in an overheated
area of the refrigerant formed in the refrigerant passage.
[0009] The above structure makes it possible to suppress heat
transfer from the refrigerant tubes to the cold storage material in
the overheated area of the refrigerant formed in the refrigerant
passage. Thus, it is possible to avoid a situation in which the
cold storage material is less cooled due to the influence of the
overheated area where the refrigerant temperature becomes high. As
a result, even when there is an overheated area, it is possible to
ensure the cold storage performance by reducing the influence of
the overheated area.
[0010] According to the present disclosure, a cold storage heat
exchanger can be provided, which can secure a cold storage
performance, while there is an overheated area, by reducing
influence of the overheated area.
BRIEF DESCRIPTION OF DRAWINGS
[0011] FIG. 1 is a block diagram illustrating a configuration of a
refrigerating cycle apparatus which uses an evaporator as a cold
storage heat exchanger according to a first embodiment.
[0012] FIG. 2 is a plan view of the evaporator as the cold storage
heat exchanger in FIG. 1.
[0013] FIG. 3 is a side view of the evaporator as the cold storage
heat exchanger in FIG. 1.
[0014] FIG. 4 is a diagram schematically illustrating a flow of
refrigerant in the evaporator.
[0015] FIG. 5 is a schematic view of the evaporator exploded into
an upstream side and a downstream side in an airflow direction.
[0016] FIG. 6 is a plan view schematically illustrating the flow of
refrigerant in the evaporator.
[0017] FIG. 7 is a graph showing a transition of a refrigerant
temperature in a refrigerant passage inside the evaporator.
[0018] FIG. 8 is a sectional view taken along a line VIII-VIII in
FIG. 3 illustrating cold storage material containers, refrigerant
tubes, and air passages.
[0019] FIG. 9 is a sectional view schematically illustrating the
shape of an inner fin which functions as a heat transfer
suppressor.
[0020] FIG. 10 is a sectional view taken along a line A1-A1 in FIG.
9.
[0021] FIG. 11 is a sectional view schematically illustrating a
modification of the shape of the inner fin.
[0022] FIG. 12 is a sectional view schematically illustrating a
modification of the shape of the inner fin.
[0023] FIG. 13 is a diagram illustrating an example in which the
flow of refrigerant differs from that illustrated in FIG. 4.
[0024] FIG. 14 is a schematic view of an evaporator illustrated in
FIG. 13 exploded into the upstream side and the downstream side in
the airflow direction.
[0025] FIG. 15 is a plan view schematically illustrating the flow
of refrigerant in the evaporator illustrated in FIG. 13.
[0026] FIG. 16 is a graph showing a transition of a refrigerant
temperature in a refrigerant passage inside the evaporator
illustrated in FIG. 13.
[0027] FIG. 17 is a diagram illustrating an example in which the
flow of refrigerant differs from that illustrated in FIG. 4.
[0028] FIG. 18 is a diagram illustrating an example in which the
flow of refrigerant differs from that illustrated in FIG. 4.
[0029] FIG. 19 is a diagram illustrating an example in which the
flow of refrigerant differs from that illustrated in FIG. 4.
[0030] FIG. 20 is a diagram illustrating an example in which the
flow of refrigerant differs from that illustrated in FIG. 4.
[0031] FIG. 21 is a sectional view schematically illustrating the
shape of a cold storage material container which functions as a
heat transfer suppressor in an evaporator according to a second
embodiment.
[0032] FIG. 22 is a sectional view taken along a line A2-A2 in FIG.
21.
[0033] FIG. 23 is a sectional view schematically illustrating a
modification of the shape of the cold storage material
container.
[0034] FIG. 24 is a sectional view schematically illustrating the
shape of a cold storage material container which functions as a
heat transfer suppressor in an evaporator according to a third
embodiment.
[0035] FIG. 25 is a sectional view taken along a line A3-A3 in FIG.
24.
[0036] FIG. 26 is a sectional view schematically illustrating a
modification of the shapes of the cold storage material container
and the inner fin.
[0037] FIG. 27 is a sectional view schematically illustrating the
shape of an inner fin which functions as a heat transfer suppressor
in an evaporator according to a fourth embodiment.
[0038] FIG. 28 is a sectional view taken along a line A4-A4 in FIG.
27.
[0039] FIG. 29 is a sectional view schematically illustrating the
shape of a cold storage material container which functions as a
heat transfer suppressor in an evaporator according to a fifth
embodiment.
[0040] FIG. 30 is a sectional view taken along a line A5-A5 in FIG.
29.
[0041] FIG. 31 is a sectional view schematically illustrating the
shape of a cold storage material container which functions as a
heat transfer suppressor in an evaporator according to a sixth
embodiment.
[0042] FIG. 32 is a sectional view taken along a line A6-A6 in FIG.
31.
[0043] FIG. 33 is a diagram schematically illustrating the flow of
refrigerant in an evaporator according to a seventh embodiment.
[0044] FIG. 34 is a schematic view of the evaporator illustrated in
FIG. 33 exploded into the upstream side and the downstream side in
the airflow direction.
[0045] FIG. 35 is a plan view schematically illustrating the flow
of refrigerant in the evaporator illustrated in FIG. 33.
[0046] FIG. 36 is a diagram schematically illustrating the flow of
refrigerant in an evaporator according to a comparative example of
the seventh embodiment.
[0047] FIG. 37 is a schematic view of the evaporator illustrated in
FIG. 36 exploded into the upstream side and the downstream side in
the airflow direction.
[0048] FIG. 38 is a plan view schematically illustrating the flow
of refrigerant in the evaporator illustrated in FIG. 36.
[0049] FIG. 39 is a diagram schematically illustrating the flow of
refrigerant in an evaporator according to a modification of the
seventh embodiment.
[0050] FIG. 40 is a plan view schematically illustrating the flow
of refrigerant in the evaporator illustrated in FIG. 39.
[0051] FIG. 41 is a diagram schematically illustrating the flow of
refrigerant in an evaporator according to a modification of the
seventh embodiment.
[0052] FIG. 42 is a plan view schematically illustrating the flow
of refrigerant in the evaporator illustrated in FIG. 41.
[0053] FIG. 43 is a sectional view schematically illustrating the
shape of an inner fin which functions as a heat transfer suppressor
in an evaporator according to an eighth embodiment.
[0054] FIG. 44 is a sectional view taken along a line A7-A7 in FIG.
43.
[0055] FIG. 45 is a sectional view taken along a line B7-B7 in FIG.
43.
[0056] FIG. 46 is a sectional view schematically illustrating the
shape of a cold storage material container which functions as a
heat transfer suppressor in an evaporator according to a ninth
embodiment.
[0057] FIG. 47 is a sectional view taken along a line A8-A8 in FIG.
46.
[0058] FIG. 48 is a sectional view taken along a line B8-B8 in FIG.
46.
[0059] FIG. 49 is a sectional view schematically illustrating the
shape of a cold storage material container which functions as a
heat transfer suppressor in an evaporator according to a tenth
embodiment.
[0060] FIG. 50 is a sectional view taken along a line A9-A9 in FIG.
49.
[0061] FIG. 51 is a sectional view taken along a line B9-B9 in FIG.
49.
[0062] FIG. 52 is a plan view schematically illustrating the flow
of refrigerant in an evaporator according to an eleventh
embodiment.
[0063] FIG. 53 is a plan view schematically illustrating the flow
of refrigerant in an evaporator according to a twelfth
embodiment.
[0064] FIG. 54 is a plan view schematically illustrating the flow
of refrigerant in an evaporator according to a thirteenth
embodiment.
[0065] FIG. 55 is a schematic view illustrating an internal
structure of a cold storage material container of an evaporator
according to a fourteenth embodiment.
[0066] FIG. 56 is a schematic view illustrating a structure of a
cold storage material container of an evaporator according to a
fifteenth embodiment.
DESCRIPTION OF EMBODIMENTS
[0067] Hereinbelow, embodiments will be described with reference to
the accompanying drawings. In order to facilitate the understanding
of description, identical elements are designated by identical
reference signs as far as possible throughout the drawings, and
redundant description will be omitted.
First Embodiment
[0068] A first embodiment will be described with reference to FIGS.
1 to 10. A refrigerating cycle apparatus 1 is used in a vehicle air
conditioner. As illustrated in FIG. 1, the refrigerating cycle
apparatus 1 includes a compressor 10, a radiator 20, a pressure
reducer 30, and an evaporator 40. These components are annularly
connected to each other through piping to constitute a refrigerant
circulation passage. In the refrigerating cycle apparatus 1, a cold
storage heat exchanger according to the first embodiment is used as
the evaporator 40. In the following description, the cold storage
heat exchanger 40 according to the present embodiment is also
referred to as the "evaporator 40".
[0069] The compressor 10 is driven by an internal combustion engine
which is a power source 2 for traveling of a vehicle. Thus, when
the power source 2 comes to a stop, the compressor 10 also comes to
a stop. The compressor 10 draws a refrigerant from the evaporator
40, compresses the drawn refrigerant, and ejects the compressed
refrigerant to the radiator 20.
[0070] The radiator 20 cools the high-temperature refrigerant. The
radiator 20 is also called a condenser. The pressure reducer 30
reduces the pressure of the refrigerant cooled by the radiator 20.
The pressure reducer 30 may be provided as a fixed orifice, a
temperature expansion valve, or an ejector.
[0071] The evaporator 40 evaporates the refrigerant with the
pressure reduced by the pressure reducer 30 and cools a medium. The
evaporator 40 cools air supplied to a vehicle cabin. The
refrigerating cycle apparatus 1 may further include an internal
heat exchanger which performs heat exchange between a high-pressure
side liquid refrigerant and a low-pressure side gas refrigerant and
a tank element such as a receiver or an accumulator which stores an
excessive refrigerant. The power source 2 may be provided as an
internal combustion engine or an electric motor.
[0072] The structure of the evaporator 40 as the cold storage heat
exchanger according to the first embodiment will be described with
reference to FIGS. 2 to 10. In the following description, an
up-down direction on the sheets of FIGS. 2 and 3 is referred to as
a "height direction", an upper side in the height direction is
referred to as an "upper side", and a lower side in the height
direction is referred to as a "lower side". Although the height
direction is typically the gravity direction, the height direction
may be another direction. A right-left direction on the sheet of
FIG. 2 is referred to as an "inflow direction" in which a
refrigerant flows, a right side in the inflow direction is referred
to as a "front side", and a left side in the inflow direction is
referred to as a "back side". A right-left direction on the sheet
of FIG. 3 is referred to as an "airflow direction" in which air
flows through an air passage 53, a left side in the airflow
direction is referred to as an "upstream side", and a right side in
the airflow direction is referred to as a "downstream side".
[0073] In FIGS. 2 and 3, the evaporator 40 includes a refrigerant
passage member which has a plurality of branches. The refrigerant
passage member is provided as a passage member made of metal such
as aluminum. The refrigerant passage member includes a first header
41, a second header 42, a third header 43, and a fourth header 44
which are positioned in pairs, and a plurality of refrigerant tubes
45 which couple the headers. The first header 41, the second header
42, the third header 43, and the fourth header 44 extend in the
inflow direction. The refrigerant tubes 45 extend in the height
direction which is perpendicular to the inflow direction.
[0074] In FIGS. 2 and 3, the first header 41 is paired with the
second header 42. The first header 41 and the second header 42 are
disposed apart from each other by a predetermined distance in the
height direction and parallel to each other in the inflow
direction. Also, the third header 43 is paired with the fourth
header 44. The third header 43 and the fourth header 44 are
disposed apart from each other by a predetermined distance in the
height direction and parallel to each other in the inflow
direction. The first header 41 and the third header 43 are disposed
on the upper side in the height direction. The second header 42 and
the fourth header 44 are disposed on the lower side in the height
direction.
[0075] A plurality of refrigerant tubes 45 are arrayed at regular
intervals between the first header 41 and the second header 42.
Each of the refrigerant tubes 45 communicates with the inside of
the first header 41 and the inside of the second header 42 at one
end thereof. The first header 41, the second header 42, and the
refrigerant tubes 45 disposed between the first header 41 and the
second header 42 form a first heat exchange unit 48.
[0076] A plurality of refrigerant tubes 45 are arrayed at regular
intervals between the third header 43 and the fourth header 44.
Each of the refrigerant tubes 45 communicates with the inside of
the third header 43 and the inside of the fourth header 44 at the
other end thereof. The third header 43, the fourth header 44, and
the refrigerant tubes 45 disposed between the third header 43 and
the fourth header 44 form a second heat exchange unit 49.
[0077] As a result, the evaporator 40 includes the first heat
exchange unit 48 and the second heat exchange unit 49 which are
disposed in two layers. In the airflow direction, the second heat
exchange unit 49 is disposed at the upstream side, and the first
heat exchange unit 48 is disposed at the downstream side. The
refrigerant tubes 45 are disposed in two rows in the inflow
direction so as to be paired in the airflow direction.
[0078] A joint as a refrigerant inlet is disposed at an end (the
end at the front side in the inflow direction) of the first header
41. As illustrated in FIGS. 4 to 6, the inside of the first header
41 is partitioned into a first section and a second section by a
partition plate which is disposed at substantially the center in
the length direction (inflow direction) of the first header 41.
Correspondingly, the refrigerant tubes 45 are divided into a first
group G1 corresponding to the first section and a second group G2
corresponding to the second section.
[0079] The refrigerant is supplied to the first section of the
first header 41. The refrigerant is distributed to the refrigerant
tubes 45 belonging to the first group G1 from the first section.
The refrigerant flows into the second header 42 through the
refrigerant tubes 45 of the first group G1 so as to be collected in
the second header 42. The refrigerant is redistributed to the
refrigerant tubes 45 belonging to the second group G2 from the
second header 42. The refrigerant flows into the second section of
the first header 41 through the refrigerant tubes 45 of the second
group G2. In this manner, a U-shaped flow passage for the
refrigerant is formed in the first heat exchange unit 48.
[0080] A joint as a refrigerant outlet is disposed at an end (the
end at the front side in the inflow direction in the present
embodiment, but may be an end at the back side) of the third header
43. As illustrated in FIGS. 4 to 6, the inside of the third header
43 is partitioned into a first section and a second section by a
partition plate which is disposed at substantially the center in
the length direction of the third header 43. The first section of
the third header 43 is adjacent to the second section of the first
header 41. The first section of the third header 43 communicates
with the second section of the first header 41. Correspondingly,
the refrigerant tubes 45 are divided into a third group G3
corresponding to the first section and a fourth group G4
corresponding to the second section.
[0081] The refrigerant flows into the first section of the third
header 43 from the second section of the first header 41. The
refrigerant is distributed to the refrigerant tubes 45 belonging to
the third group G3 from the first section. The refrigerant flows
into the fourth header 44 through the refrigerant tubes 45 of the
third group G3 so as to be collected in the fourth header 44. The
refrigerant is redistributed to the refrigerant tubes 45 belonging
to the fourth group G4 from the fourth header 44. The refrigerant
flows into the second section of the third header 43 through the
refrigerant tubes 45 of the fourth group G4. In this manner, a
U-shaped flow passage for the refrigerant is formed in the second
heat exchange unit 49. The refrigerant inside the second section of
the third header 43 flows out of the refrigerant outlet and flows
toward the compressor 10.
[0082] In the present embodiment, the refrigerant tube 45 is a
multi-hole tube which includes a plurality of refrigerant passages
inside thereof. The refrigerant tube 45 is also called a flat tube.
The multi-hole tube can be obtained by an extrusion method or a
method of bending and forming a plate. The refrigerant passages
extend in the longitudinal direction of the refrigerant tube 45,
and are open on both ends of the refrigerant tube 45. The
refrigerant tubes 45 are arranged in rows. In each of the rows, the
refrigerant tubes 45 are disposed with the principal faces thereof
facing each other. As illustrated in FIG. 8, the air passage 53 for
heat exchange with air or a storage area for storing a cold storage
material container 47 (described below) is formed between each
adjacent two of the refrigerant tubes 45.
[0083] The evaporator 40 includes a fin member for increasing the
contact area with air supplied to the vehicle cabin. The fin member
is provided as a plurality of fins 46 each having a corrugated
shape. Each of the fins 46 is disposed in the air passage 53 which
is formed between two adjacent refrigerant tubes 45. The fin 46 is
thermally coupled to the two adjacent refrigerant tubes 45. The fin
46 is joined to the two adjacent refrigerant tubes 45 with a
joining material that is excellent in heat transfer. A brazing
material can be used as the joining material. The fin 46 is made of
a thin metal plate, such as a thin aluminum plate, which is formed
into a wave shape. The fin 46 includes an air passage called a
louver.
[0084] The evaporator 40 further includes a plurality of cold
storage material containers 47. The cold storage material container
47 is made of metal such as aluminum. The cold storage material
container 47 has a flat tubular shape. The cold storage material
container 47 forms a chamber for storing a cold storage material 50
inside thereof by joining two plates having a hollow shape. The
cold storage material container 47 includes wide principal faces at
both sides thereof. Further, two principal walls which form the
respective two principal faces are parallel to the refrigerant
tubes 45. The cold storage material container 47 is disposed
between two adjacent refrigerant tubes 45.
[0085] The cold storage material container 47 is disposed between
the two refrigerant tubes 45 which are adjacent to each other in
the inflow direction. The cold storage material container 47 is
thermally coupled to the two refrigerant tubes 45 disposed on both
sides thereof. The cold storage material container 47 is joined to
the two adjacent refrigerant tubes 45 with a joining material that
is excellent in heat transfer. A brazing material or a resin
material such as an adhesive can be used as the joining material.
The cold storage material container 47 is brazed to the refrigerant
tubes 45. The brazing material is disposed between the cold storage
material container 47 and each of the refrigerant tubes 45 so as to
couple the cold storage material container 47 and the refrigerant
tubes 45 through a large sectional area. As the brazing material, a
material clad with a brazing material may be used, or a brazing
material foil may be disposed between the cold storage material
container 47 and each of the refrigerant tubes 45. As a result,
excellent heat transfer is exhibited between the cold storage
material container 47 and the refrigerant tubes 45. The surface of
the cold storage material container 47 may have recesses and
projections, and the projections may be joined to the refrigerant
tubes 45.
[0086] In FIGS. 2 and 8, the refrigerant tubes 45 are arranged at
substantially regular intervals. A plurality of spaces are formed
between the refrigerant tubes 45. The fins 46 and the cold storage
material containers 47 are arranged in the spaces with a
predetermined regularity. FIGS. 2 and 8 illustrate a structure in
which two fins 46 (air passages 53) and one cold storage material
container 47 are repeatedly arranged in this order. However, an
arrangement other than the illustrated arrangement may be employed.
Some of the spaces serve as the air passages 53. The remaining
spaces serve as the storage areas. The fins 46 are disposed in the
respective air passages 53. The cold storage material containers 47
are disposed in the respective storage areas. Each of two
refrigerant tubes 45 that are located on both sides of the cold
storage material container 47 defines the air passage for heat
exchange with air at the side opposite to the cold storage material
container 47. In another point of view, two refrigerant tubes 45
are disposed between two fins 46, and one cold storage material
container 47 is further disposed between the two refrigerant tubes
45. It is possible to transfer heat of the refrigerant to the cold
storage material 50 without receiving a heat load of air flowing
through the fin 46 by the cold storage material container 47
disposed between the two refrigerant tubes 45. Thus, the cold
storage efficiency is improved.
[0087] One cold storage material container 47 and two refrigerant
tubes 45 located on both sides of the cold storage material
container 47 constitute one cold storage unit. A plurality of cold
storage units having the same structure are arranged on the
evaporator 40. The cold storage units are arranged at regular
intervals. Further, the cold storage units are equally arranged
right and left. Furthermore, the cold storage units are
symmetrically arranged right and left.
[0088] As illustrated in FIG. 10, the cold storage material
container 47 is joined to both of the refrigerant tubes 45 of the
first heat exchange unit 48 and the second heat exchange unit 49 in
the airflow direction. As illustrated in FIG. 8, the cold storage
material container 47 includes an outer shell 47a. The outer shell
47a is made of a plate material which is formed into a flat tubular
shape. An inner fin 47b having a corrugated shape is stored in the
outer shell 47a. The inner fin 47b is made of a metal plate, such
as a thin aluminum plate, which is formed into a wave shape like
the fin 46. A plurality of tops of the inner fin 47b are brazed to
the inner faces of principal walls (the walls whose outer surfaces
are principal faces joined to the refrigerant tubes 45) on both
sides in the inflow direction of the outer shell 47a. As
illustrated in FIGS. 9 and 10, the inner fin 47b extends in the
longitudinal direction (height direction) of the cold storage
material container 47. Peaks and valleys of the inner fin 47b
extend in the airflow direction. With such a structure, the inner
fin 47b increases the contact area between the cold storage
material 50 and the cold storage material container 47. Details of
the shape of the inner fin 47b will be described below.
[0089] Hereinbelow, the first header 41 is also referred to as an
inlet side passage which includes an inlet of the refrigerant
passage. Similarly, the third header 43 is also referred to as an
outlet side passage which includes an outlet of the refrigerant
passage. The first header 41 and the third header 43 are disposed
in parallel in the airflow direction at the same position in the
height direction and collectively referred to as a first header
tank 51. Similarly, the second header 42 and the fourth header 44
are disposed in parallel in the airflow direction at the same
position in the height direction and collectively referred to as a
second header tank 52.
[0090] As schematically illustrated in FIGS. 4 to 6, a refrigerant
flowing into the first section of the first header 41 flows into
the first section of the second header 42 through the refrigerant
tubes 45 of the first group G1 (first turn). The refrigerant
flowing into the first section of the second header 42 flows into
the second section of the second header 42. The refrigerant flowing
into the second section of the second header 42 flows into the
second section of the first header 41 through the refrigerant tubes
45 of the second group G2 (second turn). The second section of the
first header 41 and the second section of the third header 43
communicate with each other. Thus, the refrigerant flowing into the
second section of the first header 41 flows into the second section
of the third header 43. The refrigerant flowing into the second
section of the third header 43 flows into the second section of the
fourth header 44 through the refrigerant tubes 45 of the third
group G3 (third turn). The refrigerant flowing into the second
section of the fourth header 44 flows into the first section of the
fourth header 44. The refrigerant flowing into the first section of
the fourth header 44 flows into the first section of the third
header 43 through the refrigerant tubes 45 of the fourth group G4
(fourth turn). The refrigerant flowing into the first section of
the third header 43 flows out to the outside. That is, the
evaporator 40 of the present embodiment is configured to include a
so-called four-turn type refrigerant passage.
[0091] As illustrated in FIG. 1, in the refrigerating cycle
apparatus 1, the compressor 10 for compressing and ejecting the
refrigerant is typically present on the downstream side in the flow
of the refrigerant relative to the evaporator 40. A return of the
refrigerant in a liquid state to the compressor 10 causes a
failure. Thus, it is typically necessary to completely evaporate
the refrigerant at an outlet of the evaporator 40. Accordingly, the
refrigerant forms a single gas layer near the outlet of the
refrigerant passage, and the pressure thereof exceeds the saturated
vapor pressure. As a result, there is a part where a refrigerant
temperature rapidly transitions to a high temperature, that is, an
overheated area S. FIG. 7 illustrates an example of the
characteristics of the refrigerant temperature in the four-turn
type refrigerant passage. The horizontal axis of FIG. 7 represents
the position in the refrigerant passage. The left side (an origin
point side) of the horizontal axis corresponds to the inlet, and
the right side thereof corresponds to the outlet. The vertical axis
of FIG. 7 represents the refrigerant temperature in each passage
position. As illustrated in FIG. 7, the refrigerant temperature
decreases after the refrigerant is introduced into the refrigerant
passage. However, the refrigerant temperature rapidly transitions
to a high temperature at a substantially intermediate position in
the fourth turn (that is, the fourth group G4), and the overheated
area S is formed in a part thereafter. For example, as illustrated
in FIG. 5, the overheated area S is formed in a substantially half
area on the upper side in the height direction in the refrigerant
tubes 45 of the fourth group G4.
[0092] As illustrated in FIG. 10, the cold storage material
container 47 is joined to both of the refrigerant tubes 45 of the
first heat exchange unit 48 and the second heat exchange unit 49 in
the airflow direction. Thus, in a conventional cold storage
material container 47, cold storage is interrupted at the
refrigerant tubes 45 of the fourth group G4, due to the influence
of the overheated area S, that is, cold storage is interrupted only
in the cold storage material 50 in a part that is in contact with
the refrigerant tubes 45 on the upstream side in the airflow
direction. Thus, there is a difference in cooling of the cold
storage material 50 inside the cold storage material container 47
between the upstream side and the downstream side in the airflow
direction. Accordingly, there may be a difference in a blowout
temperature between the back side and the front side in the inflow
direction (that is, between an area that does not include the
overheated area S and an area that includes the overheated area S)
during cold release.
[0093] In view of the above issue, in the present embodiment, as
illustrated in FIGS. 9 and 10, the inner fin 47b has a shape that
is not joined to the cold storage material container 47 in the
overheated area S of the refrigerant. In other words, in the cold
storage material container 47 which is joined to the refrigerant
tube 45 having the overheated area S, the inner fin 47b is not
joined to the inner wall surface of the outer shell 47a of the cold
storage material container 47 in a part that is in contact with the
overheated area S of the refrigerant tube 45 and is joined to the
inner wall surface in a part that is in contact with an area other
than the overheated area S of the refrigerant tube 45. In FIG. 10,
a part where the tops of the inner fin 47b are joined to the cold
storage material container 47 is indicated by solid lines, and a
part where the tops of the inner fin 47b are not joined to the cold
storage material container 47 is indicated by dotted lines.
[0094] Further, the above structure can be reworded as follows. In
the evaporator 40, the plurality of refrigerant tubes 45 include at
least two refrigerant tubes 45 disposed in the airflow direction of
air in the air passages 53. The cold storage material container 47
is joined to the at least two refrigerant tubes 45 disposed in the
airflow direction. In this case, the joined part may have recesses
and projections, and the projections may be joined to the
refrigerant tubes 45. The inner fin 47b overlaps the at least two
refrigerant tubes 45 when viewed in an array direction of the
refrigerant tubes 45 and the cold storage material container 47
(inflow direction). The cold storage material container 47 which is
joined to the at least two refrigerant tubes 45 including the
refrigerant tube 45 having the overheated area S includes a part
that is in contact with the overheated area S of the refrigerant
tube 45. When viewed in the airflow direction, the inner fin 47b is
not joined to the inner wall of the cold storage material container
47 in an area that overlaps the part, and is joined to the inner
wall of the cold storage material container 47 in the other
area.
[0095] With the above structure, the inner fin 47b is not joined to
the cold storage material container 47, that is, the refrigerant
tubes 45 in the overheated area S. Thus, heat from the overheated
refrigerant is less likely to be transferred to the inside of the
cold storage material 50. Further, the inner fin 47b itself is
disposed (is floating) inside the cold storage material container
47 also in the overheated area S. Thus, cold of the refrigerant in
a non-overheated area is transferred also to the cold storage
material 50 in the overheated area through the inner fin 47b. In
this manner, it is possible to reduce the transfer of heat in the
overheated area to the cold storage material 50 present in the
overheated area S and also possible to transfer cold in the
non-overheated area to the cold storage material 50 present in the
overheated area S. Thus, even when there is the overheated area S
in the refrigerant passage, it is possible to cool the cold storage
material 50 inside the cold storage material container 47 in an
excellent manner. Accordingly, it is possible to eliminate such an
inconvenience that the cold storage material 50 inside the cold
storage material container 47 in the overheated area S is not
cooled and there is a temperature distribution inside the
evaporator (evaporator 40) during cold release, or, in the first
place, cold storage cannot be performed due to the influence of the
overheated area.
[0096] That is, in the first embodiment, the inner fin 47b is not
joined to the cold storage material container 47 in the overheated
area S. Accordingly, the inner fin 47b functions as a "heat
transfer suppressor" which suppresses heat transfer from the
refrigerant tube 45 to the cold storage material 50 in the
overheated area S which is formed by evaporation of the refrigerant
near the outlet of the refrigerant passage. Further, the inner fin
47b having such a structure makes it possible to suppress heat
transfer from the refrigerant tube 45 to the cold storage material
50 in the overheated area S and avoid a situation in which the cold
storage material 50 is less cooled due to the influence of the
overheated area S where the refrigerant temperature becomes high.
As a result, the evaporator 40 as the cold storage heat exchanger
of the first embodiment is capable of ensuring the cold storage
performance by reducing the influence of the overheated area S even
when there is the overheated area S.
Modifications of First Embodiment
[0097] A modification of the first embodiment will be described
with reference to FIGS. 11 to 20. In the first embodiment, in the
evaporator 40, the inner fin 47b is not joined to the inner wall
surface of the outer shell 47a of the cold storage material
container 47 in the part that is in contact with the overheated
area S of the refrigerant tube 45 and is joined to the inner wall
surface in the part that is in contact with the area other than the
overheated area S of the refrigerant tube 45. However, there may be
employed another structure that makes a heat transfer amount from
the refrigerant tube 45 to the cold storage material 50 through the
inner fin 47b in the overheated area S relatively smaller than a
heat transfer amount in an area other than the overheated area S.
In other words, it may only be required to make the heat transfer
performance of the inner fin 47b in the overheated area S
relatively lower than that in the other part. For example, as
illustrated in FIG. 11, in an evaporator 401, an inner fin 471b may
be joined to an inner wall surface of an outer shell 471a of a cold
storage material container 471 with a relatively low joining ratio
in a part that is in contact with the overheated area S of the
refrigerant tube 45 and joined to the inner wall surface with a
relatively high joining ratio in a part that is in contact with an
area other than the overheated area S of the refrigerant tube 45.
The "relatively low joining ratio" indicates that the number of
peaks and valleys of the inner fin 471b that are joined to the
inner wall surface of the outer shell 471a is relatively small. The
"relatively high joining ratio" indicates that the number of peaks
and valleys of the inner fin 471b that are joined to the inner wall
surface of the outer shell 471a is relatively large. The evaporator
401 is capable of suppressing heat transfer from the refrigerant
tube 45 to the cold storage material 50 in the overheated area S by
making the heat transfer amount through the inner fin 471b in the
overheated area S relatively small or making the joining ratio
between the inner fin 471b and the cold storage material container
471 relatively low in this manner. As a result, it is possible to
obtain an effect similar to the effect of the evaporator 40 of the
first embodiment.
[0098] In the first embodiment, in the evaporator 40, the
corrugated shape of the inner fin 47b is continuous in the
longitudinal direction (height direction) of the cold storage
material container 47, that is, the peaks and the valleys of the
inner fin 47b extend in the airflow direction. However, the
corrugated shape of the inner fin 47b may be continuous in a
direction different from the above direction. For example, as
illustrated in FIG. 12, in an evaporator 402, the corrugated shape
of an inner fin 472b may be continuous in the short direction
(airflow direction) of a cold storage material container 472, that
is, peaks and valleys of the inner fin 472b may extend in the
height direction. In this case, the peaks and valleys of the inner
fin 472b are not joined to an inner wall surface of an outer shell
472a of the cold storage material container 472 in a part that is
in contact with the overheated area S of the refrigerant tube 45 in
the height direction and are joined to the inner wall surface in a
part that is in contact with an area other than the overheated area
S of the refrigerant tube 45. Accordingly, the evaporator 402 is
capable of suppressing heat transfer from the refrigerant tube 45
to the cold storage material 50 in the overheated area S. As a
result, it is possible to obtain an effect similar to the effect of
the evaporator 40 of the first embodiment.
[0099] In the first embodiment, the four-turn type has been
described as an example of the structure of the refrigerant passage
inside the evaporator 40. However, the present disclosure is not
limited thereto. For example, as illustrated in FIGS. 13 to 15,
there may be no section inside a first header 41A, a second header
42A, a third header 43A, and a fourth header 44A. In a cold storage
heat exchanger 40A illustrated in FIGS. 13 to 15, a refrigerant
flowing into the first header 41A flows into the second header 42A
through the refrigerant tubes 45 of the first heat exchange unit 48
(first turn). The second header 42A and the fourth header 44A
communicate with each other. Thus, the refrigerant flowing into the
second header 42A flows into the fourth header 44A. The refrigerant
flowing into the fourth header 44A flows into the third header 43A
through the refrigerant tubes 45 of the second heat exchange unit
49 (second turn). The refrigerant flowing into the third header 43A
flows out to the outside. That is, the cold storage heat exchanger
40A is configured to include a so-called two-turn type refrigerant
passage.
[0100] FIG. 16 illustrates an example of the characteristics of a
refrigerant temperature in the two-turn type refrigerant passage.
As illustrated in FIG. 16, the refrigerant temperature decreases
after the refrigerant is introduced into the refrigerant passage.
However, the refrigerant temperature rapidly transitions to a high
temperature at a position in the second half of the second turn,
and an overheated area S is formed in the following part. For
example, as illustrated in FIG. 14, the overheated area S is formed
in an area on the upper side in the height direction in refrigerant
tubes 45 of the second heat exchange unit 49.
[0101] The inner fin 47b of the first embodiment can also be used
in a cold storage heat exchanger that forms the flow of a
refrigerant as formed in the cold storage heat exchanger 40A and
can function as the heat transfer suppressor.
[0102] In the cold storage heat exchange 40A, there is no section
inside the first header 41A, the second header 42A, the third
header 43A, and the fourth header 44A. However, there may be more
sections inside the headers.
[0103] In a cold storage heat exchanger 40B illustrated in FIG. 17,
the inside of each of a first header 41B, a second header 42B, a
third header 43B, and a fourth header 44B is partitioned into three
sections.
[0104] A refrigerant flowing into a first section of the first
header 41B flows into a first section of the second header 42B
through refrigerant tubes 45 (first turn). The refrigerant flowing
into the first section of the second header 42B flows into a second
section of the second header 42B. The refrigerant flowing into the
second section of the second header 42B flows into a second section
of the first header 41B through refrigerant tubes 45 (second
turn).
[0105] The refrigerant flowing into the second section of the first
header 41B flows into a third section of the first header 41B. The
refrigerant flowing into the third section of the first header 41B
flows into a third section of the second header 42B through
refrigerant tubes 45 (third turn). The third section of the second
header 42B and a third section of the fourth header 44B communicate
with each other. Thus, the refrigerant flowing into the third
section of the second header 42B flows into the third section of
the fourth header 44B. The refrigerant flowing into the third
section of the fourth header 44B flows into a third section of the
third header 43B through refrigerant tubes 45 (fourth turn).
[0106] The refrigerant flowing into the third section of the third
header 43B flows into a second section of the third header 43B. The
refrigerant flowing into the second section of the third header 43B
flows into a second section of the fourth header 44B through
refrigerant tubes 45 (fifth turn). The refrigerant flowing into the
second section of the fourth header 44B flows into a first section
of the fourth header 44B. The refrigerant flowing into the first
section of the fourth header 44B flows into a first section of the
third header 43B through refrigerant tubes 45 (sixth turn). The
refrigerant flowing into the first section of the third header 43B
flows out to the outside. That is, the cold storage heat exchanger
40B is configured to include a so-called six-turn type refrigerant
passage.
[0107] The inner fin 47b of the first embodiment can also be used
in a cold storage heat exchanger that forms the flow of a
refrigerant as formed in the cold storage heat exchanger 40B and
can function as the heat transfer suppressor.
[0108] In the cold storage heat exchangers 40, 40A, 40B, the inlet
and the outlet for the refrigerant are formed on the first headers
41, 41A, 41B and the third headers 43, 43A, 43B which are disposed
on the upper side in the gravity direction (height direction). The
inlet and the outlet for the refrigerant are not limited to the
above form. The cold storage heat exchangers 40, 40A, 40B may be
configured upside down.
[0109] In a cold storage heat exchanger 40R illustrated in FIG. 18,
a first header 41R and a third header 43R are disposed on the lower
side in the gravity direction (height direction), and a second
header 42R and a fourth header 44R are disposed on the upper side
in the gravity direction.
[0110] A refrigerant flowing into a first section of the first
header 41R flows into a first section of the second header 42R
through refrigerant tubes 45 (first turn). The refrigerant flowing
into the first section of the second header 42R flows into a second
section of the second header 42R. The refrigerant flowing into the
second section of the second header 42R flows into a second section
of the first header 41R through refrigerant tubes 45 (second
turn).
[0111] The second section of the first header 41R and a second
section of the third header 43R communicate with each other. Thus,
the refrigerant flowing into the second section of the first header
41R flows into the second section of the third header 43R. The
refrigerant flowing into the second section of the third header 43R
flows into a second section of the fourth header 44R through
refrigerant tubes 45 (third turn).
[0112] The refrigerant flowing into the second section of the
fourth header 44R flows into a first section of the fourth header
44R. The refrigerant flowing into the first section of the fourth
header 44R flows into a first section of the third header 43R
through the refrigerant tubes 45 (fourth turn). The refrigerant
flowing into the first section of the third header 43R flows out to
the outside. That is, the cold storage heat exchanger 40R is
configured to include a so-called four-turn type refrigerant
passage in which the arrangement of the cold storage heat exchanger
40 is reversed in the height direction.
[0113] A cold storage heat exchanger 40RA illustrated in FIG. 19 is
upside down of the cold storage heat exchanger 40A illustrated in
FIG. 16. The cold storage heat exchanger 40RA includes a so-called
two-turn type refrigerant passage. A first header 41RA and a third
header 43RA are disposed on the lower side in the gravity direction
(height direction). A second header 42RA and a fourth header 44RA
are disposed on the upper side in the gravity direction.
[0114] A cold storage heat exchanger 40RB illustrated in FIG. 20 is
upside down of the cold storage heat exchanger 40B illustrated in
FIG. 17. The cold storage heat exchanger 40RB includes a so-called
six-turn type refrigerant passage. A first header 41RB and a third
header 43RB are disposed on the lower side in the gravity direction
(height direction). A second header 42RB and a fourth header 44RB
are disposed on the upper side in the gravity direction.
Second Embodiment
[0115] A second embodiment will be described with reference to
FIGS. 21 to 23. An evaporator 140 of the second embodiment differs
from the evaporator 40 of the first embodiment in the structure of
a heat transfer suppressor which suppresses heat transfer from a
refrigerant tube 45 to a cold storage material 50 in an overheated
area S. Specifically, as illustrated in FIGS. 21 and 22, the shape
of a cold storage material container 147 has a structure that is
not joined to the refrigerant tube 45 in the overheated area S of a
refrigerant, and the cold storage material container 147 having the
above structure functions as the heat transfer suppressor. Further,
the evaporator 140 of the second embodiment differs from the
evaporator 40 of the first embodiment also in that no inner fin is
disposed inside the cold storage material container 147.
[0116] In other words, the cold storage material container 147
which is joined to the refrigerant tube 45 having the overheated
area S is separated from the refrigerant tube 45 without being
joined to the refrigerant tube 45 in a part (area 147c) that is in
contact with the overheated area S of the refrigerant tube 45 and
joined to the refrigerant tube 45 in a part (outer shell 147a) that
is in contact with an area other than the overheated area S of the
refrigerant tube 45. FIGS. 21 and 22 illustrate, as an example of
such a structure, a shape in which the surface of the area 147c
which overlaps the overheated area S in the outer shell 147a of the
cold storage material container 147 is recessed in a direction
separating from the refrigerant tube 45.
[0117] Further, the structure can be reworded as follows. In the
evaporator 140, a plurality of refrigerant tubes 45 include at
least two refrigerant tubes 45 disposed in the airflow direction of
air in an air passage 53. The cold storage material container 147
is joined to the at least two refrigerant tubes 45 which are
disposed in the airflow direction. The cold storage material
container 147 which is joined to the at least two refrigerant tubes
45 including the refrigerant tube 45 having the overheated area S
is separated from the refrigerant tubes 45 without being joined to
the refrigerant tubes 45 in the area 147c which includes a part
that is in contact with the overheated area S of the refrigerant
tube 45 and overlaps the part when viewed in the airflow direction,
and the cold storage material container 147 is joined to the
refrigerant tubes 45 in an area 147a other than the area 147c.
[0118] With the above structure, the cold storage material
container 147 is not joined to the refrigerant tubes 45 in the
overheated area S. Thus, heat from the overheated refrigerant is
less likely to be transferred to the inside of the cold storage
material 50. Further, the cold storage material container 147
itself is in contact with a non-overheated area. Thus, cold of the
refrigerant in the non-overheated area is transferred also to the
cold storage material 50 in the overheated area S. Accordingly, the
evaporator 140 of the second embodiment is capable of achieving an
effect similar to the effect of the evaporator 40 of the first
embodiment.
[0119] The shape of the cold storage material container 147 of the
second embodiment is not limited to the above shape and may have
another structure that makes a heat transfer amount from the
refrigerant tube 45 to the cold storage material 50 through the
cold storage material container 147 in the overheated area S
relatively smaller than a heat transfer amount in an area other
than the overheated area S. In other words, it may only be required
to make the heat transfer performance of the cold storage material
container 147 in the overheated area S relatively lower than that
in the other part. For example, as illustrated in FIG. 23, in an
evaporator 1401, a cold storage material container 1471 is jointed
to the refrigerant tube 45 with a relatively low joining ratio in a
part (area 1471c) that is in contact with the overheated area S of
the refrigerant tube 45 and joined to the refrigerant tube 45 with
a relatively high joining ratio in a part (outer shell 1471a) that
is in contact with an area other than the overheated area S of the
refrigerant tube 45. The "relatively low joining ratio" indicates
that the ratio of a part joined to the refrigerant tube 45 in the
outer surface of the cold storage material container 1471 is
relatively small. The "relatively high joining ratio" indicates
that the ratio of a part joined to the refrigerant tube 45 in the
outer surface of the cold storage material container 1471 is
relatively large. The evaporator 1401 is capable of suppressing
heat transfer from the refrigerant tube 45 to the cold storage
material 50 in the overheated area S by making the heat transfer
amount of the cold storage material container 1471 in the
overheated area S relatively small or making the joining ratio
between the cold storage material container 1471 and the
refrigerant tube 45 in the overheated area relatively low in this
manner. As a result, it is possible to obtain an effect similar to
the effect of the evaporator 40 of the first embodiment.
Third Embodiment
[0120] A third embodiment will be described with reference to FIGS.
24 to 26. An evaporator 240 of the third embodiment differs from
the evaporator 40 of the first embodiment in the structure of a
heat transfer suppressor which suppresses heat transfer from a
refrigerant tube 45 to a cold storage material 50 in an overheated
area S. Specifically, as illustrated in FIGS. 24 and 25, the shape
of a cold storage material container 247 has a structure that is
not joined to the refrigerant tube 45 in the overheated area S of
the refrigerant, and the cold storage material container 247 having
the structure functions as the heat transfer suppressor. Further,
the evaporator 240 of the third embodiment differs from the
evaporator 40 of the first embodiment also in that an inner fin
247b which is disposed inside the cold storage material container
247 is joined to an inner wall surface of an outer shell 247a over
the entire area in the longitudinal direction.
[0121] In other words, the inner fin 247b extends in the
longitudinal direction (height direction) inside the cold storage
material container 247, and is joined to an inner wall of the cold
storage material container 247. The cold storage material container
247 which is joined to the refrigerant tube 45 having the
overheated area S is separated from the refrigerant tube 45 without
being joined to the refrigerant tube 45 in a part (area 247c) that
is in contact with the overheated area S of the refrigerant tube 45
and joined to the refrigerant tube 45 in a part (outer shell 147a)
that is in contact with an area other than the overheated area S of
the refrigerant tube 45.
[0122] Further, the above structure can be reworded as follows. In
the evaporator 240, a plurality of refrigerant tubes 45 include at
least two refrigerant tubes 45 disposed in the airflow direction of
air in an air passage 53. The cold storage material container 247
is joined to the at least two refrigerant tubes 45 which are
disposed in the airflow direction. The inner fin 247b overlaps the
at least two refrigerant tubes 45 when viewed in an array direction
(inflow direction) of the refrigerant tubes 45 and the cold storage
material container 247. The cold storage material container 247
which is joined to the at least two refrigerant tubes 45 including
the refrigerant tube 45 having the overheated area S is separated
from the refrigerant tubes 45 without being joined to the
refrigerant tubes 45 in the area 247c which includes a part that is
in contact with the overheated area S of the refrigerant tube 45
and overlaps the part when viewed in the airflow direction and
joined to the refrigerant tubes 45 in an area 247a other than the
area 247c.
[0123] With the above structure, the cold storage material
container 247 is not joined to the refrigerant tubes 45 in the
overheated area S. Further, the inner fin 247b which is joined to
the inside of the cold storage material container 247 is also not
joined to the refrigerant tubes 45. Thus, heat from the overheated
refrigerant is less likely to be transferred to the inside of the
cold storage material 50. The inner fin 247b itself is disposed
also inside the cold storage material container 47 in the
overheated area S. Thus, cold of the refrigerant in a
non-overheated area is transferred also to the cold storage
material 50 in the overheated area S through the inner fin 247b.
Further, the cold storage material container 247 itself is in
contact with the non-overheated area. Thus, cold of the refrigerant
in the non-overheated area is transferred also to the cold storage
material 50 in the overheated area S. Accordingly, the evaporator
240 of the third embodiment is capable of achieving an effect
similar to the effect of the evaporator 40 of the first
embodiment.
[0124] The evaporator 240 of the third embodiment may also have a
structure in which the inner fin 247b is not joined to the inner
wall surface of the outer shell 247a of the cold storage material
container 247 in a part that is in contact with the overheated area
S of the refrigerant tube 45 similarly to the first embodiment.
With the above structure, since the inner fin 247b is not joined to
the cold storage material container 247, that is, the refrigerant
tube 45 in the overheated area S, heat from the overheated
refrigerant is further less likely to be transferred to the inside
of the cold storage material 50.
[0125] The shape of the cold storage material container 247 of the
third embodiment is not limited to the above shape and may have
another structure that makes a heat transfer amount from the
refrigerant tube 45 to the cold storage material 50 through the
cold storage material container 247 in the overheated area S
relatively smaller than a heat transfer amount in an area other
than the overheated area S. In other words, it may only be required
to make the heat transfer performance of the cold storage material
container 247 in the overheated area S relatively lower than that
in the other part. For example, similarly to the structure
described in the second embodiment with reference to FIG. 23, as
illustrated in FIG. 26, in an evaporator 2401, a cold storage
material container 2471 may be jointed to the refrigerant tube 45
with a relatively low joining ratio in a part (area 2471c) that is
in contact with the overheated area S of the refrigerant tube 45
and joined to the refrigerant tube 45 with a relatively high
joining ratio in a part (outer shell 2471a) that is in contact with
an area other than the overheated area S of the refrigerant tube
45. The evaporator 2401 is capable of suppressing heat transfer
from the refrigerant tube 45 to the cold storage material 50 in the
overheated area S by making the heat transfer amount of the cold
storage material container 2471 in the overheated area S relatively
small or making the joining ratio between the cold storage material
container 2471 and the refrigerant tube 45 in the overheated area S
relatively low in this manner. As a result, it is possible to
obtain an effect similar to the effect of the evaporator 40 of the
first embodiment.
[0126] Further, when there is applied a structure that suppresses
heat transfer from the refrigerant tube 45 to the cold storage
material 50 in the overheated area S by a joining structure between
the inner fin 2471b and the cold storage material container 2471
similarly to the first embodiment, a structure similar to the
structure described in the first embodiment with reference to FIG.
11 can be applied. Specifically, as illustrated in FIG. 26, in the
evaporator 2401, the inner fin 2471b may be joined to the inner
wall surface of the outer shell 2471a of the cold storage material
container 2471 with a relatively low joining ratio in a part that
is in contact with the overheated area S of the refrigerant tube 45
and joined to the inner wall surface with a relatively high joining
ratio in a part that is in contact with an area other than the
overheated area S of the refrigerant tube 45. The evaporator 2401
is capable of suppressing heat transfer from the refrigerant tube
45 to the cold storage material 50 in the overheated area S also by
making the joining ratio between the inner fin 2471b and the cold
storage material container 2471 relatively low in this manner. As a
result, it is possible to obtain an effect similar to the effect of
the evaporator 40 of the first embodiment.
[0127] Further, similarly to the structure described in the first
embodiment with reference to FIG. 12, in the evaporator 240, the
corrugated shape of the inner fin 247b may be continuous in the
short direction (airflow direction) of the cold storage material
container 247, that is, peaks and valleys of the inner fin 247b may
extend in the height direction. Also with the above structure, the
evaporator 240 is capable of suppressing heat transfer from the
refrigerant tube 45 to the cold storage material 50 in the
overheated area S. As a result, it is possible to obtain an effect
similar to the effect of the evaporator 40 of the first
embodiment.
Fourth Embodiment
[0128] A fourth embodiment will be described with reference to
FIGS. 27 and 28. In an evaporator 340 of the fourth embodiment, the
shape of an inner fin 347b as the heat transfer suppressor differs
from the shape of the inner fin 47b in the evaporator 40 of the
first embodiment. Specifically, as illustrated in FIGS. 27 and 28,
when refrigerant tubes 45 are disposed on the upstream side and the
downstream side in the airflow direction, an overheated area S is
typically formed on the upstream side. Thus, the fourth embodiment
differs from the first embodiment in that the inner fin 347b is not
joined to a cold storage material container 347 only on the
upstream side.
[0129] In other words, in the evaporator 340, a plurality of
refrigerant tube 45 include at least two refrigerant tubes 45
disposed in the airflow direction of air in an air passage 53. The
cold storage material container 347 is joined to the at least two
refrigerant tubes which are disposed in the airflow direction. The
inner fin 347b overlaps the at least two refrigerant tubes 45 when
viewed in an array direction (inflow direction) of the refrigerant
tubes 45 and the cold storage material container 347. In the cold
storage material container 347 which is joined to the at least two
refrigerant tubes 45 including the refrigerant tube 45 having the
overheated area S, the inner fin 347b is joined to the inner wall
of the cold storage material container 347 over the entire area in
the longitudinal direction in an area overlapping the refrigerant
tube 45 having no overheated area S. Further, in an area
overlapping the refrigerant tube 45 having the overheated area S,
the inner fin 347b is not joined to the inner wall of the cold
storage material container 347 in a part that is in contact with
the overheated area S of the refrigerant tube 45 and joined to the
inner wall of the cold storage material container 347 in the other
part.
[0130] With the above structure, the evaporator 340 achieves an
effect similar to the effect of the first embodiment. Further,
since the inner fin 347b is in contact with the refrigerant tube 45
in a non-overheated area on the downstream side, cold can be
transferred from the upstream side to the downstream side. Thus, it
is possible to further suppress heat transfer from the refrigerant
tube 45 to the cold storage material 50.
[0131] Further, the various modifications described in the first
embodiment can be applied to the evaporator of 340 of the fourth
embodiment.
Fifth Embodiment
[0132] A fifth embodiment will be described with reference to FIGS.
29 and 30. In an evaporator 440 of the fifth embodiment, the shape
of a cold storage material container 447 as the heat transfer
suppressor differs from the shape of the cold storage material
container 147 in the evaporator 140 of the second embodiment.
Specifically, as illustrated in FIGS. 29 and 30, when refrigerant
tubes 45 are disposed on the upstream side and the downstream side
in the airflow direction, an overheated area S is typically formed
on the upstream side. Thus, the fifth embodiment differs from the
second embodiment in that the cold storage material container 447
is not joined to the refrigerant tubes 45 only on the upstream
side.
[0133] In other words, in the evaporator 440, a plurality of
refrigerant tubes 45 include at least two refrigerant tubes 45
disposed in the airflow direction of air in an air passage 53. The
cold storage material container 447 is joined to the at least two
refrigerant tubes 45 which are disposed in the airflow direction.
The cold storage material container 447 which is joined to the at
least two refrigerant tubes 45 including the refrigerant tube 45
having the overheated area S is joined to the refrigerant tubes 45
over the entire area in the extending direction (height direction)
in an area overlapping the refrigerant tube 45 having no overheated
area S. Further, in an area overlapping the refrigerant tube 45
having the overheated area S, the cold storage material container
447 is separated from the refrigerant tubes 45 without being joined
to the refrigerant tubes 45 in a part (area 447c) that is in
contact with the overheated area S of the refrigerant tube 45 and
joined to the refrigerant tube 45 in a part 447a other than the
area 447c.
[0134] With the above structure, the evaporator 440 of the fifth
embodiment achieves an effect similar to the effect of the second
embodiment. Further, since the cold storage material container 447
is in contact with the refrigerant tube 45 in a non-overheated area
on the downstream side, cold can be transferred from the upstream
side to the downstream side. Thus, it is possible to further
suppress heat transfer from the refrigerant tube 45 to the cold
storage material 50. Further, the capacity of the cold storage
material container 447 can be increased compared to that of the
second embodiment. Thus, it is possible to store a larger amount of
cold storage material 50.
[0135] Further, the various modifications described in the second
embodiment can be applied to the evaporator 440 of the fifth
embodiment.
Sixth Embodiment
[0136] A sixth embodiment will be described with reference to FIGS.
31 and 32. In an evaporator 540 of the sixth embodiment, the shape
of a cold storage material container 547 as the heat transfer
suppressor differs from the shape of the cold storage material
container 247 in the evaporator 240 of the third embodiment.
Specifically, as illustrated in FIGS. 31 and 32, when refrigerant
tubes 45 are disposed on the upstream side and the downstream side
in the airflow direction, an overheated area S is typically formed
on the upstream side. Thus, the sixth embodiment differs from the
third embodiment in that the cold storage material container 547 is
not joined to the refrigerant tubes 45 only on the upstream
side.
[0137] In other words, in the evaporator 540, a plurality of
refrigerant tubes 45 include at least two refrigerant tubes 45
disposed in the airflow direction of air in an air passage 53. The
cold storage material container 547 is joined to the at least two
refrigerant tubes 45 which are disposed in the airflow direction.
An inner fin 547b overlaps the at least two refrigerant tubes 45
when viewed in an array direction (inflow direction) of the
refrigerant tubes 45 and the cold storage material container 547.
The cold storage material container 547 which is joined to the at
least two refrigerant tubes 45 including the refrigerant tube 45
having the overheated area S is joined to the refrigerant tube 45
over the entire area in the extending direction (height direction)
in an area overlapping the refrigerant tube 45 having no overheated
area S. Further, in an area overlapping the refrigerant tube 45
having the overheated area S, the cold storage material container
547 is separated from the refrigerant tube 45 without being joined
to the refrigerant tube 45 in a part (area 547c) that is in contact
with the overheated area S of the refrigerant tube 45 and joined to
the refrigerant tube 45 in a part 547a other than the area
547c.
[0138] With the above structure, the evaporator 540 of the sixth
embodiment achieves an effect similar to the effect of the third
embodiment. Further, since the cold storage material container 547
and the inner fin 547b are in contact with the refrigerant tube 45
in a non-overheated area on the downstream side, cold can be
transferred from the upstream side to the downstream side. Thus, it
is possible to further suppress heat transfer from the refrigerant
tube 45 to the cold storage material 50. Further, the capacity of
the cold storage material container 547 can be increased compared
to that of the third embodiment. Thus, it is possible to store a
larger amount of cold storage material 50.
[0139] Further, the various modifications described in the third
embodiment can be applied to the evaporator 540 of the sixth
embodiment.
Seventh Embodiment
[0140] A seventh embodiment will be described with reference to
FIGS. 33 to 38. In the seventh embodiment and embodiments
thereafter, an overheated area S1 as a subject differs from the
overheated area S of the first to sixth embodiments. An evaporator
1040 (cold storage heat exchanger) according to the seventh
embodiment suppresses heat transfer from a refrigerant tube 45 to a
cold storage material 50 in the overheated area S1 which is formed
due to flow rate variations in a refrigerant passage when the flow
rate of a refrigerant is low.
[0141] First, an issue in an evaporator 2040 which includes a
conventional two-turn type refrigerant passage will be described as
a comparative example with reference to FIGS. 36 to 38.
[0142] In the evaporator 2040, a refrigerant flowing into a first
header 2041 flows into a second header 2042 through refrigerant
tubes 45 of a first heat exchange unit 48 (first turn). The second
header 2042 and a fourth header 2044 communicate with each other.
Thus, the refrigerant flowing into the second header 2042 flows
into the fourth header 2044. The refrigerant flowing into the
fourth header 2044 flows into a third header 2043 through
refrigerant tubes 45 of a second heat exchange unit 49 (second
turn). The refrigerant flowing into the third header 2043 flows out
to the outside.
[0143] In the evaporator 2040 having such a structure, when the
flow rate of the refrigerant is low, the refrigerant is likely to
flow only to refrigerant tubes 45 on the front side in the inflow
direction near an inlet of the refrigerant passage and less likely
to be supplied to refrigerant tubes 45 on the back side in the
inflow direction. Thus, when the flow rate of the refrigerant
inside the refrigerant passage is low, there is the overheated area
S1 in an area on the back side in the inflow direction. An
overheated area S2 (second overheated area) illustrated in FIG. 37
is an overheated area which is formed near an outlet and a subject
in the first to sixth embodiments.
[0144] The evaporator 1040 of the seventh embodiment is
characterized in the structure of the refrigerant passage in order
to reduce the influence of the overheated area S1 as described
above and ensure a cold storage performance of the cold storage
material 50. The evaporator 1040 is similar to the evaporator 1040
of the first embodiment in the basic structure, but differs from
the evaporator 1040 of the first embodiment in the structure of the
refrigerant passage, more specifically, in sections inside a first
header 1041, a second header 1042, a third header 1043, and a
fourth header 1044 and a mutual communication relationship
therebetween.
[0145] As illustrated in FIGS. 33 to 35, a first section and a
second section communicate with each other inside the first header
1041 differently from the first header 41 of the first embodiment.
Thus, a refrigerant supplied to the first header 1041 is
distributed to a plurality of refrigerant tubes 45 belonging to a
first group G1 and a second group G2. The refrigerant flows into a
first section of the second header 1042 through the refrigerant
tubes 45 of the first group G1 and flows into a second section of
the second header 1042 through the refrigerant tubes 45 of the
second group G2.
[0146] The second header 1042 differs from the second header 42 of
the first embodiment in that the first section and the second
section are uncommunicably sealed. Similarly, the fourth header
1044 differs from the fourth header 44 of the first embodiment in
that a first section and a second section are uncommunicably
sealed. The first section of the second header 42 which is located
on the front side in the inflow direction and the downstream side
in the airflow direction communicates with the first section of the
fourth header 1044 which is located on the back side in the inflow
direction and the upstream side in the airflow direction. The
second section of the second header 42 which is located on the back
side in the inflow direction and the downstream side in the airflow
direction communicates with the second section of the fourth header
1044 which is located on the front side in the inflow direction and
the upstream side in the airflow direction. Correspondingly, the
refrigerant flows into the first section of the fourth header 1044
from the first section of the second header 1042 and flows into the
second section of the fourth header 1044 from the second section of
the second header 1042.
[0147] A first section and a second section communicate with each
other inside the third header 1043 differently from the third
header 43 of the first embodiment. The refrigerant flowing into the
first section of the fourth header 1044 is distributed to a
plurality of refrigerant tubes 45 belonging to a third group G3.
The refrigerant flowing into the second section of the fourth
header 1044 is distributed to a plurality of refrigerant tubes 45
belonging to a fourth group G4. The refrigerant flows into the
third header 1043 through the refrigerant tubes 45 of the third
group G3 and the fourth group G4 so as to be collected therein. The
refrigerant inside the third header 1043 flows out of the
refrigerant outlet and flows toward the compressor 10.
[0148] In this manner, in the evaporator 1040 of the seventh
embodiment, the refrigerant passage has a structure that changes
the position in the inflow direction of the refrigerant introduced
from the first header 1041 on the upper side in the height
direction in a second header tank 52 on the lower side in the
height direction. That is, the position of the refrigerant
introduced from the front side in the inflow direction through the
refrigerant tubes 45 of the first group G1 is changed to the back
side in the inflow direction. Further, the position of the
refrigerant introduced from the back side in the inflow direction
through the refrigerant tubes 45 of the second group G2 is changed
to the front side in the inflow direction. As illustrated in FIGS.
33 and 35, a schematic shape of the refrigerant passage inside the
second header tank 52 is an X shape when viewed in the height
direction. Further, a schematic shape of the refrigerant passage
inside the evaporator 1040 is a crossed shape of two two-turn type
refrigerant passages. The structure of the refrigerant passage of
the seventh embodiment is referred to as a "flow change type" for
convenience.
[0149] The structure of the flow change type refrigerant passage of
the seventh embodiment can be described as follows. The evaporator
1040 includes a first header tank 51 which is formed in such a
manner that refrigerant tubes 45 communicate with the first header
tank 51 at one end side thereof and the longitudinal direction of
the first header tank 51 is aligned with the array direction
(inflow direction) of the refrigerant tubes 45 and the cold storage
material container 47 and the second header tank 52 which is formed
in such a manner that the refrigerant tubes 45 communicate with the
second header tank 52 at the other end side thereof and the
longitudinal direction of the second header tank 52 is aligned with
the inflow direction. The refrigerant tubes 45 are arranged in two
rows so as to be paired in the airflow direction of air in the air
passage 53. The inside of the first header tank 51 is divided into
the first header 1041 and the third header 1043. The first header
1041 is an inlet side passage which communicates with some of the
refrigerant tubes 45 disposed on the downstream side in the airflow
direction and includes an inlet of the refrigerant passage on one
end in the longitudinal direction thereof. The third header 1043 is
an outlet side passage which communicates with some of the
refrigerant tubes 45 disposed on the upstream side in the airflow
direction and includes an outlet of the refrigerant passage on one
end (or the other end) in the longitudinal direction thereof.
[0150] The refrigerant tubes 45 are divided into the first group
G1, the second group G2, the third group G3, and the fourth group
G4. The refrigerant tubes 45 of the first group G1 communicate with
the first header 1041 as the inlet side passage, and are disposed
on one end side in the longitudinal direction (the front side in
the inflow direction). The refrigerant tubes 45 of the second group
G2 communicate with the first header 1041 as the inlet side
passage, and are disposed on the other end side in the longitudinal
direction (the back side in the inflow direction). The refrigerant
tubes 45 of the third group G3 communicate with the third header
1043 as the outlet side passage, and are disposed on the other end
side in the longitudinal direction. The refrigerant tubes 45 of the
fourth group G4 communicate with the third header 1043 as the
outlet side passage, and are disposed on the one end side in the
longitudinal direction.
[0151] The second header tank 52 is configured to allow
communication between the first group G1 and the third group G3 and
communication between the second group G2 and the fourth group G4
and change the position of a refrigerant introduced to the front
side in the inflow direction from the first header 1041 and the
position of a refrigerant introduced to the back side in the inflow
direction from the first header 1041 to the back side and the front
side, respectively, so as to be led to the third header 1043. The
overheated area S1 is formed in the second group G2 and the fourth
group G4 of the refrigerant tubes 45 due to flow rate variations in
the refrigerant passage when the flow rate of the refrigerant is
low. With the above structure of the refrigerant passage, as
illustrated in FIG. 35, it is possible to achieve a structure in
which a single cold storage material container 47 is joined to both
of the second group G2 having the overheated area S1 and the third
group G3 having no overheated area S1. Similarly, it is possible to
achieve a structure in which a single cold storage material
container 47 is joined to both of the first group G1 having no
overheated area S1 and the fourth group G4 having the overheated
area S1.
[0152] With the structure of the flow change type refrigerant
passage as described above, even in a condition in which the
refrigerant introduced into the first header 1041 is less likely to
flow into the back side in the inflow direction, for example, when
the flow rate of the refrigerant is low, it is possible to provide
the flow of the refrigerant with a relatively high flow rate over
the entire area in the inflow direction through the refrigerant
tubes 45 of the first group G1 and the third group G3. That is, it
is possible to flow the refrigerant to the back side in the inflow
direction in an excellent manner even when the flow rate of the
refrigerant is low. A single cold storage material container 47 is
jointed to two refrigerant tubes 45 which are disposed in parallel
in the airflow direction. The refrigerant flows through one of the
two refrigerant tubes 45 with a relatively high flow rate.
Accordingly, even when the overheated area S1 is formed on the
other one of the two refrigerant tubes 45 to which the cold storage
material container 47 is joined, cold in a non-overheated area can
be transferred to the cold storage material 50 in the overheated
area S1. Thus, it is possible to cool the cold storage material 50
inside the cold storage material container 47 in an excellent
manner.
[0153] That is, the seventh embodiment is characterized in a
refrigerant passage structure 1045 in which a single cold storage
material container 47 is joined to both of the refrigerant tube 45
having the overheated area S1 and the refrigerant tube 45 having no
overheated area by changing the position in the inflow direction of
the refrigerant in the second header tank 52 by the flow change
type refrigerant passage. The refrigerant passage structure 1045
functions as a "heat transfer suppressor" which suppresses heat
transfer from the refrigerant tube 45 to the cold storage material
50 in the overheated area S1 which is formed due to flow rate
variations in the refrigerant passage when the flow rate of the
refrigerant is low. Further, the refrigerant passage structure 1045
as described above makes it possible to suppress heat transfer from
the refrigerant tube 45 to the cold storage material 50 in the
overheated area S1 and avoid a situation in which the cold storage
material 50 is less cooled due to the influence of the overheated
area S1 where the refrigerant temperature becomes high. As a
result, the evaporator 1040 as the cold storage heat exchanger of
the seventh embodiment is capable of ensuring the cold storage
performance by reducing the influence of the overheated area S1
even when there is the overheated area S1.
[0154] Further, the surface of the cold storage material container
47 may have recesses and projections, and the projections may be
joined to the refrigerant tubes 45.
Modifications of Seventh Embodiment
[0155] Modifications of the seventh embodiment will be described
with reference to FIGS. 39 to 42. In the seventh embodiment, there
has been described, as an example, one flow change type refrigerant
passage, that is, the refrigerant passage structure 1045 in which
the position in the inflow direction of the refrigerant is changed
at one location in the second header tank 52. However, another
structure that includes at least one flow change type refrigerant
passage may be employed. For example, an evaporator 1040A
illustrated in FIGS. 39 and 40 uses one flow change type
refrigerant passage in combination with a conventional two-turn
type refrigerant passage. An evaporator 1040B illustrated in FIGS.
41 and 42 uses two flow change type refrigerant passages which are
disposed in the inflow direction in combination. Further, a
plurality of flow change type refrigerant passages may be disposed
in the inflow direction. The refrigerant passages of the evaporator
1040A and the evaporator 1040B also make it possible to achieve a
structure similar to the refrigerant passage structure 1045 of the
seventh embodiment. Thus, it is possible to achieve an effect
similar to the effect of the evaporator 1040 of the seventh
embodiment.
Eighth Embodiment
[0156] An eight embodiment will be described with reference to
FIGS. 43 to 45. An evaporator 1140 of the eighth embodiment differs
from the evaporator 1040 of the seventh embodiment in that a
function of an inner fin 1147b is further provided in addition to
the structure of the seventh embodiment as the heat transfer
suppressor which suppresses heat transfer from the refrigerant tube
45 to the cold storage material 50 in the overheated area 51 which
is formed due to flow rate variations in the refrigerant passage
when the flow rate of the refrigerant is low. Specifically, as
illustrated in FIGS. 43 to 45, the evaporator 1140 of the eighth
embodiment differs from the evaporator 1040 of the seventh
embodiment in that, in a cold storage material container 1147 which
is in contact with the overheated area 51 (the back and downstream
side, the front and upstream side), the inner fin 1147b is not in
contact with the overheated area 51.
[0157] In other words, the inner fin 1147b extends in the
longitudinal direction (height direction) of the cold storage
material container 1147 inside the cold storage material container
1147. The inner fin 1147b is not joined to the inner wall of the
cold storage material container 1147 in a part where the cold
storage material container 1147 is joined to refrigerant tubes 45
of the second group G2 and the fourth group G4 having the
overheated area 51 (a cross section taken along line B7-B7 in FIG.
43). Further, the inner fin 1147b is joined to the inner wall of
the cold storage material container 1147 in a part where the cold
storage material container 1147 is in contact with refrigerant
tubes 45 of the first group G1 and the third group G3 having no
overheated area 51 (a cross section taken along line A7-A7 in FIG.
43). The inner fin 1147b functions as the heat transfer
suppressor.
[0158] With the above structure, the evaporator 1140 of the eighth
embodiment achieves an effect similar to the effect of the seventh
embodiment. Further, since the inner fin 1147b is not in contact
with the cold storage material container 1147 in the overheated
area S1, heat in the overheated area S1 is less likely to be
transferred to the cold storage material 50 inside the cold storage
material container 1147. Thus, it is possible to more appropriately
cool the cold storage material inside the cold storage material
container 1147 with cold in a non-overheated area without the
influence of the heat in the overheated area S1.
[0159] A joining structure between the inner fin 1147b and the cold
storage material container 1147 of the eighth embodiment is not
limited to the above structure and may have another structure that
makes a heat transfer amount from the refrigerant tube 45 to the
cold storage material 50 through the inner fin 1147b in the
overheated area S1 relatively smaller than a heat transfer amount
in an area other than the overheated area S1. In other words, it
may only be required to make the heat transfer performance of the
inner fin 1147b in the overheated area S1 relatively lower than the
other part. For example, similarly to the structure described in
the first embodiment with reference to FIG. 11, the inner fin 1171b
may be joined to the inner wall surface of an outer shell 1147a of
the cold storage material container 1147 with a relatively low
joining ratio in a part that is in contact with the overheated area
S1 of the refrigerant tube 45 and joined to the inner wall surface
with a relatively high joining ratio in a part that is in contact
with an area other than the overheated area S1 of the refrigerant
tube 45. It is possible to suppress heat transfer from the
refrigerant tube 45 to the cold storage material 50 in the
overheated area S1 by making the heat transfer amount through the
inner fin 1147b in the overheated area S1 relatively small or
making the joining ratio between the inner fin 1147b and the cold
storage material container 1147 in the overheated area S1
relatively low in this manner. As a result, it is possible to
obtain an effect similar to the effect of the evaporator 1140 of
the present embodiment.
[0160] Further, similarly to the structure described in the first
embodiment with reference to FIG. 12, the corrugated shape of the
inner fin 1147b may be continuous in the short direction (airflow
direction) of the cold storage material container 1147, that is,
peaks and valleys of the inner fin 1147b may extend in the height
direction. In this case, peaks and valleys of the inner fin 1147b
that are in contact with the overheated area S1 of the refrigerant
tube 45 in the airflow direction are not joined to the inner wall
surface of the outer shell 1147a of the cold storage material
container 1147, and peaks and valleys of the inner fin 1147b that
are in contact with an area other than the overheated area S1 are
joined to the inner wall surface. Also with the above structure, it
is possible to suppress heat transfer from the refrigerant tube 45
to the cold storage material 50 in the overheated area S1 and
achieve an effect similar to the effect of the evaporator 1140 of
the present embodiment.
Ninth Embodiment
[0161] A ninth embodiment will be described with reference to FIGS.
46 to 48. An evaporator 1240 of the ninth embodiment differs from
the evaporator 1040 of the seventh embodiment in that a function of
a cold storage material container 1247 is also provided in addition
to the structure of the seventh embodiment as the heat transfer
suppressor which suppresses heat transfer from the refrigerant tube
45 to the cold storage material 50 in the overheated area S1 which
is formed due to flow rate variations in the refrigerant passage
when the flow rate of the refrigerant is low. Specifically, as
illustrated in FIGS. 46 to 48, the evaporator 1240 of the ninth
embodiment differs from the evaporator 1040 of the seventh
embodiment in that the cold storage material container 1247 which
is in contact with the overheated area S1 (the back and downstream
side, the front and upstream side) is not joined to the refrigerant
tube 45 having the overheated area S1. Further, the evaporator 1240
of the ninth embodiment differs from the evaporator 1040 of the
seventh embodiment in that no inner fin is disposed inside the cold
storage material container 1247.
[0162] In other words, the cold storage material container 1247 is
separated from the refrigerant tubes 45 without being joined to the
refrigerant tubes 45 in a part that is in contact with refrigerant
tubes 45 of the second group G2 and the fourth group G4 having the
overheated area S1 (a cross section taken along line B8-B8 in FIG.
46, an area 1247c). Further, the cold storage material container
1247 is joined to the refrigerant tubes 45 in a part that is in
contact with refrigerant tubes 45 of the first group G1 and the
third group G3 having no overheated area S1 (a cross section taken
along line A8-A8 in FIG. 46, an outer shell 1247a). The cold
storage material container 1247 functions as the heat transfer
suppressor.
[0163] With the above structure, the evaporator 1240 of the ninth
embodiment achieves an effect similar to the effect of the seventh
embodiment. Further, since the cold storage material container 1247
is not in contact with the refrigerant tubes 45 in the overheated
area S1, heat in the overheated area S1 is less likely to be
transferred to the cold storage material 50 inside the cold storage
material container 1247. Thus, it is possible to more appropriately
cool the cold storage material 50 inside the cold storage material
container 1247 with cold in a non-overheated area without the
influence of the heat in the overheated area S1.
[0164] The shape of the cold storage material container 1247 of the
ninth embodiment is not limited to the above shape and may have
another structure that makes a heat transfer amount from the
refrigerant tube 45 to the cold storage material 50 through the
cold storage material container 1247 in the overheated area S1
relatively smaller than a heat transfer amount in an area other
than the overheated area S1. In other words, it may only be
required to make the heat transfer performance of the cold storage
material container 1247 in the overheated area S relatively lower
than that in the other area. For example, similarly to the
structure described in the second embodiment with reference to FIG.
23, the cold storage material container 1247 may be jointed to the
refrigerant tube 45 with a relatively low joining ratio in a part
(area 1247c) that is in contact with the overheated area S1 of the
refrigerant tube 45 and joined to the refrigerant tube 45 with a
relatively high joining ratio in a part (outer shell 1247a) that is
in contact with an area other than the overheated area S1 of the
refrigerant tube 45. It is possible to suppress heat transfer from
the refrigerant tube 45 to the cold storage material 50 in the
overheated area S1 by making the heat transfer amount of the cold
storage material container 1247 in the overheated area S1
relatively small or making the joining ratio between the cold
storage material container 1247 and the refrigerant tube 45
relatively low in this manner. As a result, it is possible to
obtain an effect similar to the effect of the evaporator 1240 of
the present embodiment
Tenth Embodiment
[0165] A tenth embodiment will be described with reference to FIGS.
49 to 51. An evaporator 1340 of the tenth embodiment differs from
the evaporator 1040 of the seventh embodiment in that a function of
a cold storage material container 1247 is also provided in addition
to the structure of the seventh embodiment as the heat transfer
suppressor which suppresses heat transfer from the refrigerant tube
45 to the cold storage material 50 in the overheated area S1 which
is formed due to flow rate variations in the refrigerant passage
when the flow rate of the refrigerant is low. Specifically, as
illustrated in FIGS. 49 to 51, the evaporator 1340 of the tenth
embodiment differs from the evaporator 1040 of the seventh
embodiment in that the cold storage material container 1247 which
is in contact with the overheated area S1 (the back and downstream
side, the front and upstream side) is not joined to the refrigerant
tube 45 having the overheated area S1.
[0166] In other words, an inner fin 1347b extends in the
longitudinal direction (height direction) of the cold storage
material container 1347 inside the cold storage material container
1347, and is joined to the inner wall of the cold storage material
container 1347 over the entire area in the longitudinal direction.
The cold storage material container 1347 is separated from the
refrigerant tubes 45 without being joined to the refrigerant tubes
45 in a part that is in contact with refrigerant tubes 45 of the
second group G2 and the fourth group G4 having the overheated area
S1 (a cross section taken along line B9-B9 in FIG. 49, an area
1347c). Further, the cold storage material container 1347 is joined
to the refrigerant tubes 45 in a part that is in contact with
refrigerant tubes 45 of the first group G1 and the third group G3
having no overheated area S1 (a cross section taken along line
A9-A9 in FIG. 49, an outer shell 1347a). The cold storage material
container 1347 functions as the heat transfer suppressor.
[0167] With the above structure, the evaporator 1340 of the tenth
embodiment achieves an effect similar to the effect of the seventh
embodiment. Further, since the cold storage material container 1347
is not in contact with the refrigerant tubes 45 in the overheated
area S1, heat in the overheated area S1 is less likely to be
transferred to the cold storage material 50 inside the cold storage
material container 1347. Further, since the inner fin 1347b is
disposed inside the cold storage material container 1347, cold in a
non-overheated side is easily transferred to the overheated area
side. Thus, it is possible to more appropriately cool the cold
storage material 50 inside the cold storage material container 1347
with cold in the non-overheated area without the influence of the
heat in the overheated area S1.
[0168] Similarly to the eighth embodiment, the evaporator 1340 of
the tenth embodiment may have a structure in which the inner fin
1347b is not joined to the inner wall of the cold storage material
container 1347 in a part (area 1347c) where the cold storage
material container 1347 is joined to the refrigerant tubes 45 of
the second group G2 and the fourth group G4 having the overheated
area S1. With the above structure, the inner fin 1347b is not
joined to the cold storage material container 1347, that is, the
refrigerant tubes 45 in the overheated area S1. Thus, heat from the
overheated refrigerant is further less likely to be transferred to
the inside of the cold storage material 50.
[0169] The shape of the cold storage material container 1347 of the
tenth embodiment is not limited to the above shape and may have
another structure that makes a heat transfer amount from the
refrigerant tube 45 to the cold storage material 50 through the
cold storage material container 1247 in the overheated area S1
relatively smaller than a heat transfer amount in an area other
than the overheated area S1. In other words, it may only be
required to make the heat transfer performance of the cold storage
material container 1347 in the overheated area S relatively lower
than that in the other part. For example, similarly to the
structure described in the second embodiment with reference to FIG.
23, the cold storage material container 21347 may be jointed to the
refrigerant tube 45 with a relatively low joining ratio in a part
(area 1347c) that is in contact with the overheated area S1 of the
refrigerant tube 45 and joined to the refrigerant tube 45 with a
relatively high joining ratio in a part (outer shell 1347a) that is
in contact with an area other than the overheated area S1 of the
refrigerant tube 45. It is possible to suppress heat transfer from
the refrigerant tube 45 to the cold storage material 50 in the
overheated area S1 by making the heat transfer amount of the cold
storage material container 1347 in the overheated area S1
relatively small or making the joining ratio between the cold
storage material container 1347 and the refrigerant tube 45
relatively low in this manner. As a result, it is possible to
obtain an effect similar to the effect of the evaporator 1340 of
the present embodiment
[0170] Further, when there is applied a structure that suppresses
heat transfer from the refrigerant tube 45 to the cold storage
material 50 in the overheated area S1 by a joining structure
between the inner fin 1347b and the cold storage material container
1347 similarly to the eighth embodiment, a structure similar to the
structure described in the first embodiment with reference to FIG.
11 can be applied. Specifically, the inner fin 1347b is joined to
the inner wall surface of the outer shell 1347a of the cold storage
material container 1347 with a relatively low joining ratio in a
part that is in contact with the overheated area S1 of the
refrigerant tube 45 and joined to the inner wall surface with a
relatively high joining ratio in a part that is in contact with an
area other than the overheated area S1 of the refrigerant tube 45.
It is possible to suppress heat transfer from the refrigerant tube
45 to the cold storage material 50 in the overheated area S1 also
by making the joining ratio between the inner fin 1347b and the
cold storage material container 1347 relatively low in this manner.
As a result, it is possible to obtain an effect similar to the
effect of the evaporator 1340 of the present embodiment
[0171] Further, similarly to the structure described in the first
embodiment with reference to FIG. 12, the corrugated shape of the
inner fin 1347b may be continuous in the short direction (airflow
direction) of the cold storage material container 1347, that is,
peaks and valleys of the inner fin 1347b may extend in the height
direction. Also with the above structure, it is possible to
suppress heat transfer from the refrigerant tube 45 to the cold
storage material 50 in the overheated area S1 and obtain an effect
similar to the effect of the evaporator 1340 of the present
embodiment.
Eleventh Embodiment
[0172] An eleventh embodiment will be described with reference to
FIG. 52. An evaporator 1440 of the eleventh embodiment differs from
the evaporator 1040 of the seventh embodiment (refer to FIGS. 33 to
35) in that, in a plurality of refrigerant tubes 45, a high-melting
point cold storage material 50A is disposed in a part that is in
contact with the second group G2 and the fourth group G4 having an
overheated area S1, the high-melting point cold storage material
50A having a relatively high melting point compared to the other
part (the first group G1 in the present embodiment), and the
high-melting point cold storage material 50A is disposed also in a
part that is in contact with the third group G3 having an
overheated area S2.
[0173] As described above with reference to FIG. 34, in the flow
change type refrigerant flow passage structure 1045, the overheated
area S1 is formed in the second group G2 and the fourth group G4 of
the refrigerant tubes 45 due to flow rate variations in the
refrigerant passage when the flow rate of the refrigerant is low.
Further, the overheated area S2 is formed near the outlet of the
third group G3 of the refrigerant tubes 45 by a mechanism similar
to that of the overheated area S of the first to sixth embodiments.
In the eleventh embodiment, the high-melting point cold storage
material 50A is stored inside each of cold storage material
containers 47 which are in contact with the refrigerant tubes 45
having the overheated areas S1, S2 (that is, the second group G2,
the third group G3, and the fourth group G4).
[0174] As illustrated in FIG. 52, in the cold storage material
container 47 that is in contact with both of the first group G1 and
the fourth group G4 of the refrigerant tubes 45, a part that is in
contact with the first group G1 (the half part on the downstream
side in the airflow direction) is filled with the cold storage
material 50 having a normal melting point, and a part that is in
contact with the fourth group G4 (the half part on the upstream
side in the airflow direction) is filled with the high-melting
point cold storage material 50A. Such a structure can be achieved,
for example, by partitioning an internal space of a single cold
storage material container 47 with a partition plate which is
embedded inside the cold storage material container 47 at a
substantially intermediate position in the airflow direction. In
the cold storage material container 47 that is in contact with both
of the second group G2 and the third group G3 of the refrigerant
tubes 45, the entire internal space thereof is merely filled with
the high-melting point cold storage material 50A.
[0175] When the melting point of the cold storage material is
increased by using the high-melting point cold storage material
50A, a temperature difference from a refrigerant which cools the
cold storage material increases. Thus, the cold storage material is
more easily cooled (more easily congealed). For example, it is
assumed that a temperature of the refrigerant in a normal area of
the refrigerant tube 45 is -3.degree. C., a temperature of the
refrigerant in the overheated areas S1, S2 of the refrigerant tube
45 is 0.degree. C., and a melting point of the cold storage
material which performs heat exchange with the refrigerant in the
normal area of the refrigerant tube 45 is 5.degree. C. In this
case, when a melting point of the cold storage material which
performs heat exchange with the refrigerant in the overheated areas
S1, S2 of the refrigerant tube 45 is substantially equal to the
melting point of the cold storage material in the normal area,
congelation of the cold storage material in the overheated areas
S1, S2 becomes relatively difficult, and the congealability of the
cold storage material in the overheated areas S1, S2 becomes lower
than that in the normal area. On the other hand, when the melting
point of the cold storage material in the overheated areas S1, S2
is made higher than the melting point of the cold storage material
in the normal area by a temperature difference (here, +3.degree.
C.) between the refrigerant in the normal area and the refrigerant
in the overheated areas S1, S2, the congealability of the cold
storage material in the overheated areas S1, S2 becomes equal to
that in the normal area. Further, when the melting point of the
cold storage material in the overheated areas S1, S2 is made higher
than the melting point of the cold storage material in the normal
area by more than the temperature difference between the
refrigerant in the normal area and the refrigerant in the
overheated areas S1, S2, the congealability of the cold storage
material in the overheated areas S1, S2 becomes higher than that in
the normal area.
[0176] As described above, the evaporator 1440 of the eleventh
embodiment has the structure in which the high-melting point cold
storage material 50A is disposed in each part that is in contact
with the refrigerant tubes 45 having the overheated areas S1, S2.
Thus, it is possible to equalize the congealability of the cold
storage materials without depending on whether the refrigerant
which performs heat exchange with the cold storage material is
located in the overheated areas S1, S2 or in the normal area.
Accordingly, it is possible to reduce the influence of the
overheated areas S1, S2 and improve the heat storage and release
performance of the evaporator 1440.
Modification of Eleventh Embodiment
[0177] In the eleventh embodiment, there has been described, as an
example, the structure in which the high-melting point cold storage
material 50A is filled inside the cold storage material container
47 that is in contact with the refrigerant tubes 45 of the third
group G3 having the overheated area S2 over the entire area of the
cold storage material container 47 in the height direction.
However, it may only be required that the high-melting point cold
storage material 50A be filled at least in a part that is in
contact with the overheated area S2. For example, the high-melting
point cold storage material 50A may be stored only in a part that
is in contact with the vicinity of the outlet side passage having
the overheated area S2 in the cold storage material container 47
that is in contact with the refrigerant tubes 45 of the third group
G3. Such a structure can be achieved, for example, by partitioning
an internal space of a single cold storage material container 47
with a partition plate which is embedded inside the cold storage
material container 47 along a part overlapping the overheated area
S2 (e.g., a quarter part of the cold storage material container 47
on the upstream side in the airflow direction and the upper side in
the height direction).
Twelfth Embodiment
[0178] A twelfth embodiment will be described with reference to
FIG. 53. An evaporator 1540 of the twelfth embodiment differs from
the evaporator 1040 of the seventh embodiment (refer to FIGS. 33 to
35) in that, in a plurality of refrigerant tubes 45, a high-melting
point cold storage material 50A is disposed in a part that is in
contact with the second group G2 and the fourth group G4 having an
overheated area 51. In other words, the evaporator 1540 of the
twelfth embodiment differs from the evaporator 1440 of the eleventh
embodiment (refer to FIG. 52) in that the high-melting point cold
storage material 50A is not disposed in a part that is in contact
with the third group G3 having an overheated area S2.
[0179] As illustrated in FIG. 53, in the cold storage material
container 47 that is in contact with both of the second group G2
and the third group G3 of the refrigerant tubes 45, a part that is
in contact with the third group G3 (the half part on the upstream
side in the airflow direction) is filled with the cold storage
material 50 having a normal melting point, and a part that is in
contact with the second group G2 (the half part on the downstream
side in the airflow direction) is filled with the high-melting
point cold storage material 50A. The structure of the cold storage
material container 47 that is in contact with both of the first
group G1 and the fourth group G4 of the refrigerant tubes 45 is
similar to that in the eleventh embodiment described above with
reference to FIG. 52.
[0180] The evaporator 1540 of the twelfth embodiment has the
structure in which the high-melting point cold storage material 50A
is disposed in the part that is in contact with the refrigerant
tube 45 having the overheated area S1 similarly to the evaporator
1440 of the eleventh embodiment. Thus, it is possible to equalize
the congealability of the cold storage materials without depending
on whether the refrigerant which performs heat exchange with the
cold storage material is located in the overheated area S1 or in
the normal area similarly to the eleventh embodiment. Accordingly,
it is possible to achieve an effect of reducing the influence of
the overheated area S1 and improving the heat storage and release
performance.
[0181] Further, in the evaporator 1540 of the twelfth embodiment,
the cold storage materials having two different melting points (the
cold storage material 50 and the high-melting point cold storage
material 50A) are stored inside the cold storage material container
47 equally in the right and left (with the same amount in the
airflow direction) corresponding to a distribution of the
refrigerant temperature (the distribution in the order from the
normal area to the overheated area S1 in the airflow direction).
With the above structure, the cold storage materials having two
different melting points are equally congealed. As a result, it is
possible to equalize a blowout temperature distribution during heat
release.
Thirteenth Embodiment
[0182] A thirteenth embodiment will be described with reference to
FIG. 54. An evaporator 1640 of the thirteenth embodiment differs
from the evaporator 40 of the first embodiment in that the cold
storage material in a part that is in contact with the overheated
area S is a high-melting point cold storage material 50A.
[0183] As described above with reference to FIG. 5, in the
so-called four-turn type refrigerant passage structure, the
overheated area S is formed by evaporation of a refrigerant in the
substantially half area on the upper side in the height direction
in the refrigerant tubes 45 of the fourth group G4, that is, near
the outlet of the refrigerant passage. In the thirteenth
embodiment, the high-melting point cold storage material 50A is
stored in each cold storage material container 47 that is in
contact with the refrigerant tube 45 having the overheated area S
(that is, the fourth group G4).
[0184] In the thirteenth embodiment, it may only be required that
at least the cold storage material in a part that is in contact
with the overheated area S be the high-melting point cold storage
material 50A. For example, the high-melting point cold storage
material 50A may be filled inside the cold storage material
container 47 that is in contact with the refrigerant tube 45 of the
fourth group G4 having the overheated area S over the entire area
in the height direction of the cold storage material container 47
or may be filled only in a part that is in contact with the
overheated area S.
[0185] The evaporator 1640 of the thirteenth embodiment has the
structure in which the high-melting point cold storage material 50A
is disposed in the part that is in contact with the refrigerant
tube 45 having the overheated area S1 similarly to the evaporator
1440 of the eleventh embodiment. Thus, also in the four-turn type
refrigerant passage structure, it is possible to equalize the
congealability of the cold storage materials without depending on
whether the refrigerant which performs heat exchange with the cold
storage material is located in the overheated area S1 or in the
normal area similarly to the flow change type refrigerant flow
passage structure 1045 of the eleventh embodiment. Accordingly, it
is possible to achieve an effect of reducing the influence of the
overheated area S and improving the heat storage and release
performance. The structure of the third embodiment can also be
applied to the second to sixth embodiments relating to the
four-turn type refrigerant passage structure.
Fourteenth Embodiment
[0186] A fourteenth embodiment will be described with reference to
FIG. 55. An evaporator 1740 of the fourteenth embodiment differs
from each of the above embodiments in that a pair of partition
plates 47d which partitions an internal space of the cold storage
material container 47 in the longitudinal direction (that is, the
height direction) which is the extending direction of the
refrigerant tubes 45 is disposed inside the cold storage material
container 47.
[0187] As illustrated in FIG. 55, one of the partition plates 47d
(the right plate in FIG. 55) has a space in an end on one side in
the longitudinal direction (the lower side in the height direction
in FIG. 55) of the cold storage material container 47. Further, the
other one of the partition plates 47d (the left plate in FIG. 55)
has a space in an end on the other side in the longitudinal
direction (on the upper side in the height direction in FIG. 55) of
the cold storage material container 47. The partition plates 47d
are disposed at substantially regular intervals in the airflow
direction. Further, the cold storage material container 47 is
provided with a cold storage material filling pipe 47e on one of
side walls in the airflow direction that is closer to the right
partition plate.
[0188] The cold storage material 50 is filled into the cold storage
material container 47 through the cold storage material filling
pipe 47e. At this time, an approximately 15% of space is typically
left on the upper side of the inside of the cold storage material
container 47 without completely filling the internal space of the
cold storage material container 47 with the cold storage material
50 as a countermeasure against expansion by freezing. For example,
as illustrated in FIG. 55, a space having an approximately height
C1 is left on the upper end in the internal space. The overheated
areas S1, S2 described in the above embodiments are mainly formed
on the upper side in the height direction of the refrigerant tubes
45. Thus, in a conventional structure, the upper side in the height
direction of the cold storage material container 47 may be less
cooled, and a cooling failure may occur.
[0189] In the structure of the fourteenth embodiment, the internal
space of the cold storage material container 47 is partitioned into
three areas by the pair of partition plates 47d, and the
partitioned areas lie in a line in series. Thus, when the cold
storage material 50 is injected with an approximately 15% of space
left as a countermeasure against expansion by freezing in a manner
similar to a conventional manner, as illustrated in FIG. 55, a
space 47f is formed only in an area communicating with the cold
storage material filling pipe 47e, and each of the other two areas
on the back side is filled with the cold storage material 50 over
the entire area in the height direction thereof. That is, although
a height c2 from the upper end is larger than a conventional height
c1 when only the space 47f is viewed, there is no position where
the cold storage material 50 is not present in the height direction
when the entire internal space of the cold storage material
container 47 is viewed. In other words, when the internal space of
the cold storage material container 47 is viewed in the airflow
direction, the cold storage material 50 is disposed over the entire
area in the height direction. Accordingly, it is possible to
prevent formation of a space on the upper end inside the cold
storage material container 47 and eliminate an uncooled part on the
upper side in the height direction of the cold storage material
container 47.
[0190] It may only be required that at least a pair of partition
plates 47d be disposed inside the cold storage material container
47, and a plurality of pairs of partition plates may be
provided.
Fifteenth Embodiment
[0191] A fifteenth embodiment will be described with reference to
FIG. 56. An evaporator 1840 of the fifteenth embodiment differs
from the evaporator 40 of the first embodiment in that the cold
storage material container 47 which is joined to the refrigerant
tube 45 having the overheated area S is not disposed in a part that
is in contact with the overheated area S of the refrigerant tube 45
and disposed only in a part that is in contact with an area other
than the overheated area S of the refrigerant tube 45.
[0192] As described above with reference to FIG. 5, in the
so-called four-turn type refrigerant passage structure, the
overheated area S is formed by evaporation of a refrigerant in the
substantially half area on the upper side in the height direction
in the refrigerant tubes 45 of the fourth group G4, that is, near
the outlet of the refrigerant passage. In the fifteenth embodiment,
as illustrated in FIG. 56, the cold storage material container 47
that is in contact with the refrigerant tube 45 having the
overheated area S, that is, the refrigerant tube 45 of the fourth
group G4 is not disposed in an area having the overheated area S
(the vicinity of the outlet of the refrigerant passage).
[0193] With the above structure, the evaporator 1840 of the fifth
embodiment is capable of cutting heat exchange between the
refrigerant and the cold storage material 50 in the overheated area
S and improve the cooling efficiency. Accordingly, it is possible
to further improve fuel consumption by increasing an off time of an
air conditioner during an idle stop of a vehicle equipped with the
evaporator 1840 by facilitating congelation of the cold storage
material 50 to increase cooling time as compared to a conventional
product. The structure of the fifteenth embodiment can also be
applied to the second to sixth embodiments relating to the
four-turn type refrigerant passage structure.
[0194] The embodiments of the present disclosure have been
described above with reference to concrete examples. However, the
present disclosure is not limited to the concrete examples
described above. That is, the concrete examples with design
modifications appropriately added by those skilled in the art are
also included in the scope of the present disclosure as long as
they have features of the present disclosure. For example, each
element included in each of the concrete examples, and the
arrangement, material, condition, shape, and size thereof are not
limited to the illustrated one and can be appropriately modified.
Further, elements included in the respective embodiments described
above can be combined as long as the combination is technically
feasible. These combinations are also included in the scope of the
present disclosure as long as they have the features of the present
disclosure.
[0195] For example, the method described in the first to sixth
embodiments for reducing the influence on cold storage by the
overheated areas S, S2 which are formed by evaporation of the
refrigerant near the outlet of the refrigerant passage can be
combined with the structures of the seventh to tenth
embodiments.
[0196] In the above embodiments, there has been described, as an
example, the structure in which, in the evaporator 40, the cold
storage material container 47 is disposed between two refrigerant
tubes 45 and joined to the two refrigerant tubes 45, and the air
passage 53 is formed on the opposite side of the cold storage
material container 47 in each of the refrigerant tubes 45. However,
the present disclosure is not limited to the above structure. For
example, the refrigerant tubes 45 and the cold storage material
containers 47 may be formed as integrated members extending in the
same direction, and the air passages 53 may be formed in spaces
between these members.
[0197] In the above embodiments, there has been described, as an
example, the structure in which the cold storage material 50 is
stored in the cold storage material container 47. However, the
present disclosure is not limited to the above structure. For
example, the cold storage material 50 may not be stored in the cold
storage material container 47, but may have direct contact with the
refrigerant tube 45 so as to directly transfer heat from the
refrigerant tube 45 to the cold storage material 50.
* * * * *